KR20140094498A - Piston-chamber combination-vanderblom motor - Google Patents

Abstract

A chamber 186 defined by the inner chamber wall 185 and at least one chamber 186 which is sealingly moveable relative to the chamber between a first longitudinal position 208 and a second longitudinal position 208 ' Wherein the chamber has a cross-section of a circumferential length that is different from the cross-sectional area at the first longitudinal position and a cross-sectional area that is at least substantially continuously different from the cross-sectional area at the second longitudinal position, the piston has a resilient As shown in Fig. The piston is manufactured to have a manufacturing size of the vessel in a stress-free, unstrained state. Comprising: means for introducing fluid from a position (210) outside the container into the container, thereby enabling pressurization of the container, thereby expanding the container, wherein the smooth surface of the wall of the actuator piston Continuing to at least close to the contact area with the chamber wall to displace the vessel from the second longitudinal position to the first longitudinal position of the chamber.

Description

[0001] Piston-chamber combination - VANDERBLOM MOTOR [0002]

19627

A chamber bounded by an inner chamber wall and a piston provided within the chamber wall to be relatively movable in a mating state relative to the chamber wall at least between first and second longitudinal positions of the chamber, - chamber combination, wherein the chamber comprises cross-sections having different cross-sectional areas and different circumferential lengths in the first and second longitudinal positions of the chamber, and wherein the intermediate species between the first and second longitudinal positions Wherein the cross-sectional areas and circumferential lengths at the directional positions are at least substantially continuously different, the cross-sectional area at the first longitudinal position is greater than the cross-sectional area at the second longitudinal position, and the actuator piston is in alignment with the chamber wall The container comprising a container having an elastically deformable container wall for contacting, Sectional area and circumferential lengths of the piston in accordance with the different cross-sectional areas and different circumferential lengths of the chamber while passing through the intermediate longitudinal positions of the chamber and relative movement between the first and second longitudinal positions Wherein the container is elastically deformable such that the actuator piston has a circumferential length of the actuator piston substantially equal to a circumferential length of the chamber in the second longitudinal position, The piston-chamber assembly being produced in the same size as the production size of the piston-chamber assembly.

19627

The present invention addresses a solution for actuators with efficient functions as an alternative to conventional actuators and deals with the ability of the motors, more specifically the motors of the vehicle, to cope with climate change, an important goal of such actuators . In addition, the present invention addresses solutions to efficient shock absorbers and pumps.

The present invention more particularly relates to solutions to the motor acquisition problem that can not compete with the motors of the prior art based on the above combustion techniques as well as not using the combustion techniques of oil derivatives such as gasoline and light oil . This solution also aims to obtain a motor that can compete with H ₂ or even atmospheric combustion motors to meet the need to reduce CO ₂ emissions, and in the case of such motors, No new distribution networks are needed to provide energy sources.

The combustion motors based on oil derivatives are, according to today's technical standards, only an optimized version of the concept about a century ago. This is because motors as described above are not only pollutants that cause emissions of toxic gases such as CO, as well as gases such as CO ₂ , which is a major cause of climate change, among other gases, , Which means that it no longer meets today's living standards. In addition, the combustion motors tend to be heavy in weight, so that the transport weight ratio (ratio of the weight of one occupant to the total weight of the transporter) is approximately 12 (small car) to 33 (limousine, 4 Wheel drive vehicle).

In the case of new combustion motors based on H ₂ or even the atmosphere, there is a lack of a distribution network for transportation to energy sources for the motors, such as today's gas stations for the transportation of gasoline, light oil and NLG gas. Even in the case of motors of the current technology of the atmosphere-based operating type, there is a need for "filling" stations to provide the high pressure air required for large, heavy weight cylinders, The reason is that the atmosphere-based working motor is also configured to be able to operate based on, for example, combustion means such as gasoline or diesel. Therefore, it is possible to return to the Otto Motor again, but this should be prevented.

Construction of the supply chain of the above-mentioned new means used as combustion materials requires considerable financial investment, and there are difficulties with the Catch 22 situation: without the proper supply chain, the distribution of the motors as described above can not be achieved, The reason is that no one will buy these motors because of the lack of availability, and nobody will want to invest in those motor supply chains until proof is given that there is a market. For the rapid introduction and wide distribution of pollution-free motors, it is necessary to separate the motors as described above from the supply chains for providing energy sources. The home charging station for H ₂ , which is currently being developed, is interesting and seemingly tricky because it is a very dangerous gas and should only be handled by an expert.

19627

It is an object of the present invention to provide a combination of pistons and chambers for use in pumps, actuators and shock absorbers, and to provide for the use of the actuators in the motor, amongst others.

19627

In a first aspect, the present invention relates to a combination of a piston and a chamber,

The combination includes means for allowing fluid to flow from a position external to the piston into the interior of the container, thereby enabling a pressurizing action of the container, and also expanding the container so that the second and first longitudinal directions Thereby causing the container to be displaced between positions.

The classical actuator piston is disposed inside a straight cylinder, and the piston includes a piston rod. The piston is moved as a result of the pressure difference between the opposite sides of the piston, and the piston described above may be a piston comprised of an inelastic material and comprising at least one seal ring for sealing the piston against the cylinder wall. The piston is moved relative to the cylinder within the seal ring. The piston rod may be guided by bearings on one side or both sides of the cylinder. The piston rod outside the cylinder can pull out or push out the external device. The piston rod can also engage with the crankshaft, causing rotation about the crankshaft axis, which can result in, for example, movement of the vehicle including the actuator and the crankshaft.

When arranged in the interior of a straight cylinder, the actuator piston may also be an inflatable piston, for example a container type piston according to claims 5, 28 and 34 of EP 1 179 140 B1. When the interior of the inflatable piston is in a pressurized state, the piston, preferably the reinforcing wall, can be mated with the wall of the cylinder or sealed against the wall of the cylinder, and also with respect to the piston movement within the cylinder It can act in the same manner as the above-mentioned classical piston arranged inside the linear cylinder. In order to make this movement possible, it may be necessary to provide a valve on both sides of the piston, for example on the wall of the chamber, and also preferably by means of a predetermined pressure difference controlled by the control means, A fluid flow can be made on both sides of the piston. A change in the magnitude of the pressure value inside the container wall described above may only affect the ability to align or seal the wall of the piston to the wall of the chamber. However, due to friction between the walls of the container and the walls of the chamber, the internal pressure can affect the kinetic velocity of the piston.

An actuator according to the present invention is a piston chamber assembly with an expandable piston. Preferably, the interior of the piston may be provided with a fluid and / or foam under a predetermined pressure and the shape of the piston and / or the shape of the piston by the wall of the piston including the predetermined material (s) and preferably the reinforcement (s) Or size of the piston, and preferably the piston can move within the chamber without the need for fluid within the chamber and / or without pressure differentials of the fluid or foam on both sides of the piston inside the chamber, The opposite is also possible. Of course, the fluid inside the chamber may also be present, for example, for control purposes, for example at atmospheric pressure.

Another essential parameter is that the wall of the chamber is not parallel to the central axis of the chamber and that the angle of the chamber wall in the intended direction of motion of the piston has a positive value, Can be inflated. This expansion is preferably achieved by providing a first piston of the piston with the longest circumferential length of the piston from the second longitudinal position of the piston corresponding to the production size of the piston in the circumferential direction of the piston, Directional position (see EP 1 384 004 B1).

When the container is inflated, the movement of the piston can be initiated by a force applied to the inner chamber wall of the container type piston. Thus, the motion can be initiated by reaction forces exerted from the walls of the chamber to the walls of the container. These forces are the reaction of the inflation of the container wall and the inflation may be caused by the volume of the fluid inside the piston and / or by the volume of fluid within the piston due to the additional inflow of fluid from the inflated position of the outside of the piston through the enclosed space to the container. This can result in increased pressure.

In operation of the piston prototype according to Figs. 7a to 7c (WO 2004/031583) with the stiffener of Fig. 8d (WO 2004/031583), on the basis of the atmospheric pressure existing on both sides of the piston inside the chamber By a variation velocity inside the chamber of a shape having a so-called constant maximum operating force (WO 2008/025391 - Fig. 6) at a pressure value bar inside the piston which is already slightly exceeding, and from the second longitudinal position in the first longitudinal direction The piston is fired from the second longitudinal position to the first longitudinal position even when the load is not applied due to the variation angle of the positive value between the center axis of the chamber and the inner chamber wall in the direction of the position. The speed fluctuation that the piston experiences as described above is described below.

The contact between the walls of the container and the walls of the chamber may be in a matched or sealed state. As evidenced by the prototype, this contact is largely dependent on the load applied on the piston rod. In the case where no load is applied to the actuator, the contact may be made in a matched state rather than a sealed state. In the case where a load is applied to the actuator, the driving forces applied to the container are greater than when the load is not applied to the actuator. The reason for this is that sufficient force can be applied from the walls of the container onto the chamber walls, so that the contact between the walls is sealed. It can also be seen that during the movement of the piston, the contact with the wall of the chamber can be made sequentially in a mating state and in a sealed state.

The piston can move for the following reasons. The longitudinal component of the reaction force from the wall of the chamber to the wall of the container applied to the first longitudinal piston position is less than the longitudinal component of the frictional force between the wall of the piston and the wall of the chamber to which the second longitudinal piston position is applied , The resulting total force is applied toward the first longitudinal piston position, resulting in the piston moving from the second longitudinal position to the first longitudinal position. Preferably, as the one end of the container closest to the second longitudinal piston position is fastened to the piston rod by the cap 192, the piston rod also moves. A self-propelling actuator has been developed which can be an alternative to a piston that moves by the pressure difference between the outside of the piston and the inside of the chamber. Preferably, the other end of the container is slidable on the piston rod by a cap 191, which, due to the expansion of the container, causes the cap 191 to move toward the cap 192 on the piston rod, Which means that the caps 191 and 192 move closer to each other. This movement is due to the selected stiffener of the container wall and the stiffener is preferably a layer of reinforcing strings extending from the cap 191 to the cap 192 and extending parallel to the central axis of the chamber (E. G., WO 2004/031583, Fig. 8d) and optionally arranged at a slight angle with the central axis of the chamber and / or at least two reinforcement layers are arranged at a very small angle Intersect.

This is because the wall has a positive slope with respect to the center axis of the chamber in the direction of the first longitudinal piston positions and because the contact surface of the wall of the chamber and the piston is preferably resiliently deformable of the piston The movement results in the expansion of the container wall due to the fact that it is arranged longitudinally below the intermediate point, optionally just below the intermediate point of the elastically deformable wall of the piston. Thus, the original contact area between the walls becomes larger, and the frictional force increases. As the total force applied toward the first piston position decreases, the motion may be slowed down.

By virtue of this movement, the cap 191, i.e. the movable end of the piston, is brought into contact with the cap 192 which is fastened to the piston rod, substantially simultaneously with the expansion of the wall of the container between the increased contact area and the movable cap Move closer. This may be due to the overpressure still present inside the container (it may be necessary for the volume of the enclosed space to be constant during movement from the second longitudinal piston position to the first longitudinal piston position) Quot; is also inflated) is formed in a more circular shape at the portion closest to the second longitudinal position. This means that the wall of the container rolls over the chamber wall and the contact area moves toward the first longitudinal positions, thereby increasing the component of the reaction force of the wall of the chamber relative to the wall of the container. As a result, the component of the force exerted on the first longitudinal piston positions increases rapidly and becomes larger than the friction component, so that the piston moves closest to the second longitudinal piston position with the speed increasing toward the first longitudinal piston positions By moving a portion of the container such that the non-removable cap 192 moves together, the piston rod, i. E. The piston, moves from the second longitudinal piston position to the first longitudinal piston position.

Overpressure based on atmospheric pressure is measured because the piston can be placed inside the closed chamber, preferably in communication with the periphery of the combination, which may be lower than atmospheric pressure, Since pressure may need to be applied on both sides of the piston.

A fluid may be provided in the interior of the chamber communicating with the enclosure chamber space instead of the enclosure chamber space so that fluid within such a chamber does not interfere with such movement of the piston. This concept can be used in shock absorbers.

Whether or not an enclosed chamber space or channel is required for the ambient environment with atmospheric pressure depends on the ability of the piston to seal against the walls of the chamber. As 100% sealing of the piston against the chamber wall may not be required (as it is in mating), leakage from the wall to the piston may also be caused and may occur. Thus, the channels connecting the spaces of the chamber on each side of the container can be interconnected by the channels that the piston contains.

The piston may include an enclosed space, for example, a hollow piston rod. The inside of the piston can communicate with the enclosed space. The volume of the enclosed space may be constant or variable and may be adjustable. The enclosed space can communicate with a pressure source.

In a second aspect, the present invention relates to a combination of a piston and a chamber,

The piston chamber combination further comprises means for draining fluid from the container through the enclosed space to a position external to the piston to enable contraction of the container.

During the return portion of the piston stroke, the movement from the first longitudinal position to the second longitudinal position can be made in at least three possible ways. The traditional method is to seal the piston against the wall of the chamber. However, this movement is in a way that the energy cost is high, because when the container type piston is contracted and the internal volume decreases, the excess fluid inside the piston can be transported toward the enclosed space and the internal pressure of the enclosed space is increased I can do it. To save energy, the piston can mate with the chamber wall, but does not seal the chamber wall, thereby reducing the frictional force between the piston and the chamber wall. The last method can be done in a manner that sucks and drains fluid from the container during this part of the stroke to reduce the internal pressure of the container. This movement can be achieved by control means for controlling the pressure of the enclosed space.

In a third aspect, the present invention relates to a combination of a piston and a chamber,

A piston is movable relative to the chamber wall from at least a first longitudinal position to a second longitudinal position of the chamber.

It may be possible to move the piston from the first longitudinal position to the second longitudinal position without matching the piston with the chamber wall. This movement is achieved by applying a pressure within the piston to a minimum level, e.g., no stress is applied to the wall of the piston, and the circumferential length of the piston is less than or equal to the circumferential length of the piston, so that the piston can reach the second longitudinal position without jamming. To a level that is equal to the production size at the time of production (for example, atmospheric pressure).

In the fourth and fifth aspects, the present invention relates to a combination of a piston and a chamber,

Wherein the piston includes a piston rod including the enclosed space,

The piston includes a matching means outside the chamber.

In order to guide the piston during this part of the stroke, without the guiding action of the piston itself, when the piston is not aligned with the wall of the chamber, the suspension of the piston rod is, for example, Depending on the type, it can be spherical.

The piston rod can extend in the longitudinal direction from the piston and is guided by the bearing at one end of the chamber. This means that the piston rod can include an enclosing space and can also include, for example, matching means disposed outside the chamber. When the piston moves from the second longitudinal position to the first longitudinal position, the matching means can be pulled out or pushed out. Conversely, the registration means may not be pulled out or pulled out. The piston can be driven from the first longitudinal position to the second longitudinal position by an external force applied to the piston. When the piston does not move from the first longitudinal position to the second longitudinal position in a sealed state, if the piston includes a piston rod, the piston can be driven by a force applied to the piston rod. This driving can be achieved by the matching means.

However, it may also be possible for the piston to include a piston rod extending in two longitudinal directions, usually one piston rod being formed continuously with the other piston rod. One piston rod or both piston rods may include, for example, matching means disposed outside the chamber. When both ends of the piston rod can extend outside the chamber, one bearing of the piston rod can be firmly fastened to the chamber, while the other can be installed in a floating manner with respect to the chamber. When the piston moves from the second longitudinal position to the first longitudinal position, the registration means can be simultaneously pulled out and pushed out. Conversely, during the return stroke, the registration means may not be pulled out or pushed out. The piston can be driven from the first longitudinal position to the second longitudinal position by an external force applied to the piston. If the piston includes a piston rod, the piston may be driven by a force applied to the piston rod when the piston may not move from the first longitudinal position to the second longitudinal position in a sealing manner relative to the chamber. This driving can be achieved by the matching means.

In a sixth and a seventh aspect, the present invention relates to a combination of a piston and a chamber, wherein the piston rod is connected to the crankshaft,

The crank is configured to convert the motion of the piston between the second longitudinal position and the first longitudinal position of the chamber into rotational movement of the crank,

The crank converts the rotational movement of the crank into a movement of the piston from the first longitudinal position to the second longitudinal position of the piston.

The matching means may be a crankshaft connected to the piston by the piston rod. In order to be able to initiate the movement of the piston at least from the first longitudinal position to the second longitudinal position of the chamber, the crankshaft, which is caused by the movement of the piston from the second longitudinal position to the first longitudinal position, The crankshaft must be rotated before the movement is started by the piston so that the impact of the opposite weight of the crankshaft can be transmitted to the piston.

As another option, movement of the piston between the first and second longitudinal positions may be controlled by, for example, moving the piston simultaneously from the second position of the chamber to the first position (where at least two cylinders are on the same crankshaft Or by the movement of the crankshaft initiated by the other piston chamber combination (which also works together).

The initial motion of the piston may be, for example, made by an electric motor, which initiates rotation of the crankshaft to maintain rotation of the crankshaft for a short time until the crankshaft is rotated by the piston chamber combination Is a kind of starter motor.

In seventh and eighth aspects, the present invention relates to a combination of a piston and a chamber, wherein the piston rod is connected to the crankshaft,

The crankshaft includes a second containment space,

The second enclosed space communicates with the power source.

The crankshaft may be hollow and may include a second containment space. This means that the crankshaft axis and its counterweights are also formed hollow in such a way as to form a channel from the container type piston towards the end of the crankshaft axis. These channels can communicate with the pressure source by the O-ring seal.

Further, the channel may be disposed within the crankshaft including the axial bearing of the crankshaft, so that it may communicate with an external power source.

In a ninth aspect, the present invention relates to a combination of a piston and a chamber,

The second enclosed space communicates with the first enclosed space of the piston rod during a period of time in which the piston moves from the first longitudinal position to the second longitudinal position of the chamber.

During the travel from the first longitudinal position to the second longitudinal position during stroke, the pressure of the piston may be reduced to a predetermined pressure level at the time of production of the piston, And connecting the first enclosed space inside the piston with the second enclosed space inside the crankshaft for the time period required to move to the second longitudinal position. The pressure level at the time of piston production may be any pressure level other than atmospheric pressure. When the first and second enclosed spaces are connected to each other, the higher the pressure level, the lower the energy loss.

In a tenth aspect, the present invention relates to a combination of a piston and a chamber,

The crankshaft includes a third enclosed space in communication with the first enclosed space of the piston rod for a period of time during which the piston moves from the second longitudinal position to the first longitudinal position of the chamber.

This third containment space has the function of repressurizing the piston when the direction of movement is changed from the final second longitudinal position of the chamber toward the first longitudinal position of the chamber. This pressurizing action is achieved by connecting the third enclosed space in the overpressure state with respect to the first enclosed space to the first enclosed space. The pressing action can be made quickly as soon as the direction of motion of the piston is changed.

In an eleventh aspect, the present invention relates to a combination of a piston and a chamber,

The third enclosed space communicates with the second enclosed space during a period of time in which the piston moves from the second longitudinal position to the first longitudinal position of the chamber.

In the shock absorber,

A combination according to all of the above aspects,

- means for mating with the piston from a position external to the chamber,

The matching means has an outer position in which the piston is in the first longitudinal position of the chamber and an inner position in which the piston is in the second longitudinal position.

The shock absorber may further include an enclosed space communicable with the container. The enclosed space may have a variable volume or a constant volume. This volume may be adjustable.

The shock absorber may include a container and an enclosure space, wherein the enclosure space may form an at least substantially sealed cavity comprising a fluid, wherein the fluid is in fluid communication with the piston from a first longitudinal position of the chamber to a second longitudinal position It can be compressed.

The pump for pumping the fluid comprises means for mating with a second piston inside the second chamber from a position external to the chamber, a fluid inlet connected to the second chamber and comprising valve means, and a second chamber connected to the second chamber And may include a fluid outlet.

The matching means of the pump may have an external position in which the piston may be in the first longitudinal position of the chamber and an internal position in which the piston may be in the second longitudinal position of the chamber.

The matching means of the pump may have an outer position in which the piston may be in the second longitudinal position of the chamber and an inner position in which the piston may be in the first longitudinal position of the chamber.

The technique of the piston-chamber combination can be used for a motor, specifically a motor vehicle, more particularly a self-propelled actuator.

The piston may also be movable relative to the tapered wall within a chamber, which may be cylindrical or conical (not shown).

The chamber in which the piston (actuator) piston is disposed may be of a type that may include a convexly shaped inner wall of the longitudinal section section near the first longitudinal position, the section being divided by a common boundary And the distance between the two subsequent common boundary sections defines the height of the walls of the sections with said longitudinal cross section, said heights decreasing as the internal overpressure ratio of said piston increases, And the lateral length of the common boundary portions of the cross section can be determined by a maximum operating force that can be selected to be a constant value for each of the common boundary portions.

In addition, the chamber may include a wall of a cross-sectional boundary parallel to the central axis of the chamber.

In addition, the piston-chamber combination may comprise a transition between the convexly shaped walls and the parallel wall, and when the transition can comprise a wall of at least concave shape, Directional position.

In addition, the piston-chamber combination may comprise a concave shaped wall, at least one side of the concave shaped wall being disposed in a convexly shaped wall.

19627 - Preliminary investigation

A preliminary investigation of the 'green' motor is as follows - see Figures 10b and 11b which provide a good overview of the issue. In this system, the output of the motor is generated by a new propulsion system, and the expandable actuator piston inside the chamber continuously changing its cross-sectional area is moved from a position having the smallest cross-sectional area to a position having a larger cross- . During the return stroke, the fluid in the actuator piston is also depressurized. The fluid is recompressed by a cascade pumping system using an energy efficient piston-chamber combination according to WO 2000/070227. At least one step in this repressurization process is achieved by energizing by an external green power source, e.g., the sun, or preferably another environmentally friendly power source, or alternatively, a non-environmentally friendly power source. More efficient and reliable solutions can be seen in Figures 11g and 13f. Such a system meets the above-mentioned specifications.

The " green " motive power source for a motor based on the principle of FIG.

According to the overall system solution according to the present invention, said 'green' motor as described above may be based on comparable components as used in combustion engines of the state of the art, It may be necessary to have significantly more efficient and much more functions than the combustion motors' functions and the energy used is preferably a 'green' energy source, such as, for example, the sun, For example, by combustion of H ₂ generated when operated by electrolysis, or alternatively may be obtained from an H ₂ rechargeable storage tank + fuel cell and / or pressure storage vessel, And / or from a battery. Also, the energy used may be obtained in the system itself, and preferably may be obtained from another power source, preferably because the required energy may be less than the total effective energy that allows the system to perform the exercise task have. The above-described pressure storage container is preferably provided with a pressurized fluid of a low pressure (e.g., about 10 bar), optionally a high pressure (e.g., less than 300 bar) And the pressurized fluid is also preferably re-pressurized during operation of the motor, and optionally recharged upon shutdown of the motor. The battery described above is charged at the time of production of the motor, preferably continuously recharged at the time of operation of the motor, and / or optionally recharged at the time of non-operation of the motor.

According to the piston-chamber combination technique disclosed in WO 2000/070227, energy savings of up to 65% for a considerable amount of energy, for example, a pump of 8 bar pressure (operating pressure of a motor vehicle of the current technology) Can be achieved. For example, a pressure inside the tube of 10 mm in diameter with a diameter of 17 mm (60 mm in the first longitudinal position) at the second longitudinal piston position, and a region with the smallest cross sectional area of the chamber at the second longitudinal piston Position, the highest pressure is generated in the second longitudinal position. Conversely, by using the above technique, the same efficiency can be achieved even in the case of an actuator instead of a pump. WO 2004/031583 discloses an inflatable piston type (for example, an ellipsoidal ↔ spherical body: a small spherical body ↔ a large spherical body), and a piston of this type, Does not cause a pinching phenomenon in the chamber when the circumferential length of the piston of the piston is substantially equal to the circumferential length of the portion having the smallest cross-sectional area of the chamber (which may correspond to the second longitudinal position). This type of piston represents a special feature for use as an actuator piston in the chamber, and this feature is claimed in the present invention. That is, the actuator is self-propelled. When the piston is pushed through the enclosed space by a pressure supplied from a pressure source outside the chamber at the second longitudinal position and there is no pressure difference between the opposite sides of the piston inside the chamber, , The actuator piston is moved to the first longitudinal piston positions with the largest cross-sectional area within the chamber designed to have a constant maximum value of 260 N when operating the prototype, and when the angle between the central axis of the piston is 260 N (See WO 2008/025391 and WO 2009/083274). As this phenomenon can be applied to the aforementioned 'green' motor, the exchange of motion can be made based on the energy derived from the combustion techniques, although still using the crankshaft. The energy of use due to the expansion can correspond to, for example, approximately 5 bar of the ellipsoid-spherical body (for example, an overpressure of 10 bar to 5 bar due to an increase in the volume of the piston) by a constant volume of enclosed space (WO 2009/083274). This pressure drop has to be recovered in the system because during the return stroke the actuator piston needs to be in a non-stressed state at the second longitudinal piston position corresponding to the size at the time of production, For example, If the enclosed space of the piston is connected to another enclosed space, an overpressure of 5 bar at the first longitudinal piston positions can be re-used, and the other enclosed space can be reused, for example, inside the crankshaft And the pressure increases again from 5 bar to 10 bar through a two-stage pumping process, for example. This can be accomplished effectively using piston-chamber combination techniques of other embodiments disclosed in WO 2000/070227, so that in a re-pressurization process, and also, for example, further developments are claimed in the present invention Using the piston according to claim 1 of EP 1 179 140 B1 or the piston according to Figs. 5a to 5h of WO 2000/065235, for example, an energy of 65% can be saved. In addition to this 65% energy reduction, additional energy savings can be achieved by connecting the crankshaft of the pump to the main crankshaft of the actuator piston: an additional 35% energy savings can be achieved . Thus, the total savings is 76.7% (65 + 1/3 x 35%). Thus, for example, 23.3% of energy from the same pump as described above should be obtained, but is currently being supplied with energy from an electric motor receiving electricity from the battery. The battery can be, for example, optionally charged by a solar cell (a solar cell which is not larger than the roof of a general vehicle or is contained in the paint of the vehicle), or alternatively by a fuel cell, Preferably by an alternator. The alternator can obtain a rotational force from the axis of the small H ₂ internal combustion engine or from the axis of the system of the motor itself. The energy required to perform the pump function is 35%, or 8.2%, of 23.3%.

The motor may not generate heat or noise, and the weight of such a motor is substantially less than the weight of the current combustion motor (e.g., 60% level). Not only does it require the control of the water temperature for cooling purposes and the control of the oil temperature and the exhaust system, as well as the need for combustion motors, but also because of the gasoline tank the body is made of aluminum and / or plastic The weight of the future vehicle may be half the weight of vehicles of the current technology. For example, the weight of the VW Golf Mark II is 836 kg, whereas the weight of the vehicle designed and manufactured according to the present invention is approximately 425 kg, and the TWR is only 6.3 when the driver is only boarded.

In one case, when the solar cell can be used alone for recharging the battery, it is a problem to operate for a long time in a dark night. However, the light of the street lamps on the downtown roads may be sufficient to provide the light needed by the solar cell.

Also, a transmission may be required because the number of revolutions of this 'green' motor may be lower than the number of revolutions of the combustion motors of the present technology.

19627 - Added to (corrected) content - Preliminary investigation at 19618

Preliminary investigations to date have not quantitatively included a lack of heat generated by the motors of the present invention, as compared to Otto motor types.

The motor type of the present invention is still more interesting and persuasive even when heat loss may be involved. For the current Otto motors, efficiency can be 25% due to heat loss. As a first example, if it can be assumed that the motor of this type of the invention does not generate any heat (isothermal state), the fluid may be fed from 5 bar to 10 bar Of the energy available to press) to about < RTI ID = 0.0 > 65%. ≪ / RTI > The total efficiency of a motor of the type according to the invention may be less than 10%, i.e. less than 8.75%, by self-propelled actuator pistons, and this efficiency may be unprecedented up to now (David JC McKay David JC Mackay's Sustainable Energy without High Temperature Air. If the pressure regeneration pump shown in the present invention uses a piston-chamber combination of the type according to the invention, another 65% energy can be saved. As a result, ignoring the heat generated by the pump, the total energy usage may be 8.75% x 0.875 = 7.6%. However, if some of the energy used for pumping is different from other energy sources, such as a battery that is charged by solar energy (photovoltaic cells) and / or a fuel cell (e.g., H ₂ ) , The use energy of the regenerative braking device or flywheel coupled to the generator can be terminated at less than 10%, as compared to the total energy used.

As already concluded at the outset, the configuration of the motor of the type according to FIG. 11g, 15c or 15d, and 13f and 13g and 14d can be most efficient (simple configuration, with nearly isothermal thermodynamic properties 13f, 13g, and 14d are not used, and the configuration of Fig. 13f is used for the quantitative evaluation of the motor vehicle.

For the current technology of the present invention, VW Golf Mark II model RF (1600 cc), the weight is 836 kg, the 53 kW / 71 pk gasoline motor is used, the diameter is 81 mm and the pressure is 9 bar And four cylinders with a stroke of 77 mm. In this case, the maximum force per cylinder is 1159 N, which corresponds to approximately 116 kg per cylinder. When all the combustion parts are removed from the vehicle body and the body is made of aluminum rather than steel, a weight reduction of about 50% can be assumed. Thus, when four passengers are loaded with luggage, a force of 58 kg per cylinder may be required to drive the aluminum bodywork.

The maximum operating force of the chamber of the pump shown in WO 2008/025391 is 260 N (26 kg), with a total stroke of approximately 400 mm and a diameter of 58 mm to 17 mm at a pressure of 2 bar to 10 bar. When an expandable elliptical piston is used in such a chamber, the actuator can actually perform a fairly good function. Thus, two of the chambers currently being used as part of the actuator may be equivalent to one cylinder of the gasoline motor of the VW Golf Mark II, wherein the gasoline motor of the VW Golf Mark II is formed of aluminum, And all the parts associated with it have been removed.

In the motor according to the present invention, the pressure of the enclosed space of the actuator piston is approximately 0 bar (stroke: first longitudinal position to second longitudinal direction) at x bar (stroke: second longitudinal position? First longitudinal position) Position). To limit energy usage, the value of "x" can be chosen to be as small as possible. Since the magnitude of the operating force is independent of the pressure value when using the particular type of chamber, limiting the pressure using a pressure window ranging from the highest level of 3.5 bar to the lowest level of about 0.5 bar It can be possible.

The starting points may follow the pressure configuration of the spherical body piston disposed in the rotary chamber of Figure 13f. However, 3½ bar uses only a portion of the stroke (216.2 mm of 400 mm) in the particular chamber, and the force per actuator piston is up to 260 N, so a chamber of simpler shape now compared to the chamber shown in FIG. Can be used.

The spheres may exhibit a significantly large volume change: V ₂ = 4/3 x 3.14 x 12.55 ³ (diameter 25.1 mm; P ₂ = 0.35 N / mm ² ) = 8280 mm ³ to V ₁ = 4/3 x 3.14 x 23.45 ³ (diameter 46.9 mm; P ₁ = 0.05 N / mm ² ) = 54015 mm ³ , ΔV = 6.5, and ΔP = 7. The angle between the central axis of the chamber and the wall is: L ₁ = 302.78 - 86.57 = 216.21,? R = 10.9: angle = 2.9 (this angle value is good).

The volume of the actuator piston at the first longitudinal position (index 1) is "virtual" in volume at the second longitudinal position (index 2) with respect to the complete one stroke (L ₁ ) The energy used to compress is W _isotherm = -P ₁ V ₁ ln (P ₂ / P ₁ ) = 0.35 x 54015 x In 7 = 0.35 x 54015 x 2.302585 x log 7 = 36788 Nmm / channel / piston / revolution = 36.8 J / channel / piston / revolution number. The motor according to the present invention is not as fast as the gasoline motor (900 revolutions per minute) with respect to the number of strokes per minute, because the home expansion and contraction rate of the actuator piston formed of reinforced rubber is slower. Assuming 60 revolutions per minute, it is 1 rotation per second (15x slower than in the combustion motor). W = 36.8 J / channel / piston / second. 2 x 4 'comparable' chambers (cylinders) are provided and the power is 294.3 J / s per piston, which translates to 0.295 kW per piston. When five pistons are used, each of the five sub-chambers is disposed in each of the 360 ° channels (FIG. 13F), and the generated power may be 5 x 0.295 kW = 1.47 kW.

Assuming a revolution per second, as shown at the beginning of this investigation, the power of the combustion gasoline motor can be saved at 53 kW, 92.4%, and only 7.6%, 4.03 kW can be used. If the number of revolutions per second is approximately rounded to three rotations per second, then, first, such a motor can comply with the calculations described above.

Thus, a motor comprising 2 x 4 "comparable " chambers and each chamber comprising five pistons in five subchambers is capable of rotating about 3 rotations per second (= 180 revolutions per minute) And this power may be sufficient to drive the VW Golf Mark II made of an aluminum body.

As indicated in the literature (David Jaysie McKay's environmentally friendly energy without high temperature air, 127p, Fig. 20.20 / Fig. 20.21), a small electric vehicle uses approximately 4.8 kW of power for operation and 8 x 6 V Of the battery, and can run 77km with one battery charge, which takes several hours to charge. When the energy source is batteries, such batteries are not chargeable during driving of the vehicle. These energy sources are only one choice and not a preferred embodiment.

How much energy is needed to pressurize and depressurize the actuator pistons and can this depressurization and pressurization be achieved during vehicle operation?

It is necessary to achieve a pressure change in the actuator pistons of the motor in a pressurized state. The principles shown in Figs. 11F and 13F are used.

Energy can be obtained from the kinetic energy provided in the rotating chambers, and in these rotating chambers, for example, a piston of a classical piston-chamber combination is moved by a camshaft in communication with the main motor shaft of the motor do. When using the data used to calculate the motor power, the pressure change of the inflatable spherical body piston can be made by changing the volume of the enclosed space of the actuator piston by changing the volume of the 'below' classical piston.

The volumetric variation of each piston required for the actuator piston to move from the second longitudinal position to the first longitudinal position is thus a small spherical body shape (25.1 mm in diameter) at an intermediate internal pressure (3.5 bar) ) To a larger spherical body shape (diameter 46.9 mm) under a low pressure (0.5 bar). In this case, the volume of the enclosed space is kept constant by the internal pressure change of the actuator piston. Regardless of the internal force, the piston's force per unit force is 260 N, so that if there are eight chambers each containing five pistons and the number of revolutions per second is 3, the generated power is 4.4 kW.

The energy required to reach the second longitudinal position from the first longitudinal position (Figs. 14A and 14B)

1. The shape of the actuator piston (diameter: 46.9 mm: 0.5 bar) was produced in the form of production (diameter 25.1 mm: 0) by deflating the actuator piston into the measuring enclosure where the volume is now increasing bar (overpressure)). In this way, if the frictional force between the pump piston and the wall of the containment space is sufficiently small, no energy cost can be avoided at all.

2. Energy is required to inflate a spherical body (diameter 25.1 mm, 0 bar) to a spherical body (diameter 25.1 mm, 3.5 bar) by reducing the volume of the enclosure space where the pump piston moves close to the actuator piston:

W _isotherm = -P ₁ V ₁ ln (P ₂ / P ₁ ) = -1 (confirmed) x 4/3 x 3.14 x 12.55 ³ x In 4.5 * / 1 = -1 x 8280 x 2.302585 x log 4.5 = 12454 For a 2 x 4 chamber, five actuator pistons are provided per chamber and the number of revolutions per second is 3 = 12.5 x 8 x 5 x 3 Js = 1.5 kW (* P ₁ = Nmm / channel / piston / For an absolute pressure of 1 bar, the P ₂ absolute pressure is 4.5 bar).

Thus, the total generated power is 4.4 kW, and the power required to achieve motor operation is at least 1.5 kW, thus requiring approximately 2 kW in addition to the other final losses.

To approach the motor, compare the pump to the effective pump if a pump meeting the above needs to be present in the vehicle. Compressors of the state of the art have the following specifications: 220 V, 170 l / min, 2.2 kW, 8 bar, and a 100 liter pressure storage vessel. Although power is required, since it is low pressure, the compressor thus modified charges the pressure storage vessel somewhat faster.

Since P = 2200 W at 8 bar, a pressure of 3½ bar may be required when using the same repressurization time as at 8 bar, so the required power is only 3/8 x 2200 = 825 W. Even if the battery is a 24 V battery, the current is 825/24 = 34.4 A, which is a considerable amount for one battery and consequently the pump indicated by reference numeral 826/831 should be electrically operated A plurality of batteries are available in the motor configurations shown in Figs. 11A, 11B and 11G and Figs. 12A and 13A. These batteries may be chargeable only by an external power source, so they are inefficient for a long time use vehicle and therefore the capacitor solution (Figure 15e) is still in the research stage. This is only an option, not a preferred embodiment.

It may be better to prevent power conversion and also to ensure that the pump 826/831 is connected to a combustion motor using, for example, H ₂ , which is preferably generated by electrolysis, Lt; RTI ID = 0.0 > 15c < / RTI > The process described above uses electricity from a battery that is charged by an alternator in communication with the shaft as a power source.

There is a need to generate 825 W of power by the combustion motor, which is a classic 24 cc / 66 cc motor using an Otto cycle that can be compared to currently used large moped motors (The VW Golf Mark II has a 4-cylinder motor with 53 kW, 1600 cc, 90 mm diameter, and 825 W corresponds to approximately 24 cc, 90 mm, one cylinder, or 3x faster , 2.2 kW corresponds to approximately 66 cc, 90 mm, one cylinder). Mopeds have been on television a couple of months ago, using electrolysis of water stored in tanks (the original gasoline tank) and using H ₂ generated for the combustion process - these mopeds are feasible. For a vehicle, an external motor, really is the auxiliary motor is formed in such a size, the required equipment in order to prevent any excess combustion equipment is unfortunately sources or CO ₂ emissions have been removed in the beginning from the VW Golf Mark II in order to reduce the weight , The noise can be successfully reduced by appropriate noise reduction measurements, the motor weight is reduced to 15 liters (= 15 kg) of water tank and the vehicle weight 1/6 (= about 35 kg) - the feasibility study of these motors may still be in progress.

19627 End, 19611 added to description Correction - Preliminary investigation at 19618

Further development of a way to maximize the generated force of the piston and minimize the inflating force (= pressure drop) by moving the inflatable piston in the chamber of a specific design can be further developed. Also, the movement interruption or " hesitation behavior " of the piston (see page xx) can be compensated for by the corrected internal shape of the chamber.

As a new aspect, control of the motor according to the first principle based on Fig. 1A is described for one actuator piston-chamber combination per crankshaft as follows.

The pressure storage vessel is assumed to be pressurized by an external pressure source, once and throughout the motor's production process. The actuator piston can be started by an electric starter motor using a battery charged by the solar cell, and / or by a classic dynamo rotated by the main shaft of the motor. The starter motor initially rotates the crankshaft and as a result of this movement the interior of the actuator piston is pressed and the movement of the actuator piston is subsequently initiated by the actuation of the actuator piston and consequently the rotation of the crankshaft / RTI > Then, the starter motor can be separated from the crankshaft.

Also, by opening the pressure storage vessel 814, the motor may be started to pressurize the interior of the actuator piston by the fluid 822 to initiate movement of the piston (see FIG. 1B).

The increase in the speed of the motor, in other words, the increase in the rotational speed of the crankshaft, causes the so-called reduction valve between the pressure vessel of the (lead) line 829 and the actuator piston to open . The reduction of the rotational speed of the crankshaft can be achieved by closing the reduction valve in the open state by reducing the pressure inside the actuator piston.

Additional power supply to the motor (supply of rotational force on the main shaft) may be accomplished by increasing the pressure of the actuator piston-chamber combination of the existing configuration, or more than one actuator piston-chamber combination may be provided per shaft. The shutdown of the motor may be accomplished by fully closing the reduction valve of the (lead) line 829. The reducing valve can communicate with the speed regulating device.

More detailed pressure management of the actuator piston may be configured as follows. Holes can be formed in both the wall of the crank of the crankshaft and the end of the piston rod, and these holes communicate with the second enclosed space and the third enclosed space and with the other enclosed space, respectively. The holes can communicate with each other at a predetermined time so that the enclosed space of the actuator piston can communicate with the second or third enclosed space inside the crankshaft .-- While communicating with the second enclosed space, And can be moved from the second longitudinal position to the first longitudinal position within the chamber. During communication with the third containment space, shrinkage of the piston may occur if the piston can be moved from the first longitudinal position to the second longitudinal position. Due to the relative default positions of each of the crankshaft of the pump and the crankshaft of the actuator piston that can be assembled on the same axis, the pressure in the third enclosed space inside the crankshaft is reduced by the main piston pump 818 And the pressure reduction of the enclosed space of the piston rod is started.

The pressure management that can be done in the actuator piston which operates as follows is described in more detail below. A hole provided in the final second longitudinal position of the piston can be filled .

One or more actuator piston-chamber assemblies of the motor may be coaxial. However, this concept may not help to meet these specifications. In the current situation, it is possible to make the operation of the motor more smooth by providing one or more piston-chamber assemblies per shaft, by the combustion motors of the present technology. Of course, the torque applied on the axis is increased.

How is the operation done, one crankshaft Party  Configured Actuator  piston/ chamber  What is the relationship between the combinations?

The crankshaft itself may be inefficient in the manner of generating rotational motion, and the length of one stroke of this type of piston-chamber combination may be, for example, longer than the length of one stroke of the combustion motor of the present technique. In other words, the number of revolutions of the crankshaft may be substantially different from the number of revolutions of the combustion motor of the present technology. Gears may be required and the gear ratio may be different from the gear ratios of the combustion motors of the current art. The efficiency of the transmission may be reduced by 25% and the efficiency may be improved (by 50%) using low friction bearings such as fluid dynamic bearings. Since the motor can be operated for the entire operating time, a clutch may be required. Therefore, 33.2% of the energy required by the vehicle motor must be supplied from, for example, solar energy, for example, from solar energy on the paint / vehicle hood / loop of the entire body of green energy , The amount may be significant. Of course, some special batteries can be added only if they are charged by energy from wind or solar energy. This battery addition increases the dead load of the vehicle and increases the WTR ratio. The battery as described above requires a partially flow-through structure. Thus, this type of motor may not be fully compliant with these specifications, for example, when pursuing a 'green' vehicle motor.

Therefore, in order to meet the specifications, the gear as well as the crankshaft can be excluded.

The " green " motor rotational power source < RTI ID = 0.0 >

At some point, the piston can be rotated instead of translational motion, and this new type of motor can be a kind of "green" Wankel motor.

At least for propulsion systems, using the same principle as described above, better energy use can be achieved by the motor without the crankshaft. By reducing the distance from the first rotational position of the piston inside the chamber to the second rotational position to approximately the radius level of the piston so that the motor can supply power to the shaft substantially continuously, This reduced amount of energy can be used, especially in a chamber centered on a swivel center line that can be arranged concentrically around the main axis of the motor.

The conical chamber, in which the piston can function as a self-propelling actuator, can be bent in a circular direction in the longitudinal direction and filled over 360 degrees or a portion thereof. At least one piston may function within the chamber. The motor may include one or more actuator piston-chamber assemblies that can use the same shaft. An axis may be provided at the center of the circular motion of the actuator piston and / or the chamber, which may be connected to a component, such as a wheel, e.g. a propeller, which allows the vehicle or other transport means to be driven.

There are two ways to construct these motors. One is a method in which the central axis of the actuator piston rod is extended in the plane in which the central axis of the chamber is located. Another possibility is to consider a configuration in which the central axis of the actuator piston rod can be arranged perpendicular to the plane in which the central axis of the chamber is located. In both cases, the actuator piston and / or chamber can move.

As the chamber can be bent in a circular shape in the longitudinal direction, a piston formed in the interior of the circularly folded chamber so as to deform its shape from ellipsoidal to spherical and vice versa (see, for example, WO 2000/070227 - , Figs. 9B and 9C), it seems that the actuation of the actuator piston as used in the elongated conical chamber is not possible, thereby omitting the bearing of the piston rod of the actuator piston.

Instead, a type of actuator piston of a type that is deformed from a sphere (smaller in size) to a sphere (larger in size), and vice versa, (e.g., WO 2002/077457, Figs. 6A- 9A to 9C) can be used. Such a piston can make the configuration of the bearings of the piston rod less complicated due to the symmetrical shape. For example, the piston rod may be disposed through the actuator piston in a direction perpendicular to the plane in which the center axis of the chamber is formed.

Due to the fact that it is now circular, but the chamber is of the same shape as the straight chamber that was used when using the translational piston, the actuator piston can move inside the chamber.

However, a straight line extending from the center of the piston to a location where the chamber and the piston are matched (and / or sealed) and a wall portion of the piston located behind the translational center axis of the piston in a direction perpendicular to the center axis of the chamber , The size is substantially smaller than the size of the ellipsoidal-spherical piston which translates on the central axis of the elongated chamber. This is because it is assumed that the power of each actuator piston (sphere-sphere) can be lower than the power of the ellipsoidal-sphere actuator piston. This applies to motors in which more than one actuator piston per chamber is used. Additional issues apply to the same motor because the actuator pistons are moved discontinuously (see below) and one or more pistons within the same 360 deg. Chamber can cause smooth motion. In addition, when the actuator piston (s) is inflated to a maximum extent, the pressure inside the actuator piston is reduced in a very short moment, and because of this moment, one actuator piston is also displaced from the other actuator piston In order to overcome the 'hesitation' phenomenon during exercise, it is possible to provide a 'moment of hesitation' in motion. The actuator pistons may be disposed at different locations on the central axis of the chamber. As an example, when a chamber in the range of 360 degrees is divided into four identical sub-chambers, the number of actuator pistons is five, based on equally divided over 360 degrees.

The main advantage of such a rotary motor is that the length of the return stroke from the first position to the second position on the circular path of the actuator piston is substantially reduced as compared to the crankshaft option, 2 position is directly related to each other in the rotational direction, the radius of the piston at the first circular position is at least the maximum.

Therefore, it may be necessary to manage the pressure drop inside the actuator piston and the pressure rise immediately thereafter.

There are two basic ways to change the internal pressure of the actuator pistons. According to one embodiment, each of the actuator pistons can be connected by a channel to a valve that can increase / decrease the pressure inside the actuator pistons. The valves can be adjusted by the computer such that the pressure inside the actuator piston has an optimum value at the piston position within the chamber. The computer can also be configured to adjust the pressure supplied from the pressure vessel serving as a pressure source, so as to optimize the use of the effective fluid pressure of the actuator pistons through the distribution of the effective pressure of each of the actuator pistons . According to the second approach, for example, the volume of the enclosed space varies over a very short time. This change can be made, for example, by a movable piston which is sealingly connected to the wall of the elongate chamber. The chamber may be of a type having a different cross-sectional area in the translation direction. Due to the speed of travel, this chamber may be of a constant circumferential length type so that only the piston is bent during operation. However, of course, a chamber having different circumferential lengths at the transition portion may be optionally used. The piston moving inside the chamber may have a piston rod that can communicate with a cam disk that can be connected to a shaft on which the motor is mounted. At the end of the piston rod, a wheel rolling on the cam disc may be provided. Therefore, in this type of motor there is no fluid consumption and only the contained energy (pressure) of the fluid is consumed.

A 360 ° chamber can rotate about an axis, and the center axis of this axis can intersect the center of the chamber. The chamber may constitute a part of the wheel and a notch may be provided on the outer side of the wheel so that a drive belt, which may be a drive assist device such as an electric generator, may be arranged inside the notch.

Obviously, for a type of motor in which the chamber rotates and the piston (s) do not move, a less complex solution than a solution of the two options of rotatable motors is presented. Further, in this solution, since more than 5x pistons of the same dimension are provided per chamber, a larger amount of torque, for example, a torque of 5x is generated.

The most reliable system may be a system in which the piston is fixed inside the rotating chamber. As an advantage, the motor may comprise one or more pistons, for example five pistons, each of which can be arranged in different rotational positions, with this advantage, the piston is moved from the first rotational position to the second rotational position Can be achieved by, for example, being powered by four different pistons, thus ensuring smooth rotation of the motor. Also, the "bouncing behavior" (see below) of the piston during its transition from the second rotational position to the first rotational position can also be supported by, for example, four different pistons, Exercise may not be observed.

As the pressure ratio of the fluid inside the piston defines the speed of the main shaft, the transmission may be unnecessary. With such a motor configuration, the required pressure window can be easily obtained, and such pressure can be easily defined by the speed regulating device. Thus, the transmission may be overconfigured and the weight of approximately 50 kg may be further reduced. In the case of the VW Golf Mark II, conversion is further reduced to approximately 350 kg. TWR is approximately 5.6.

Control of the rotary motor is done in a manner similar to the control of a motor with a translational piston (or even a motor with a translational motion chamber and a non-moveable piston, or even a type of motor (not shown) in which the chamber and the piston both move) .

Control means function execution, start, acceleration, deceleration, start, stop, and stop of motor.

The functioning of the motor can be effected by an electric on / off switch which is switched in the electrical system and another switch which connects the starter motor to the electric circuit so that the motor is connected to the shaft and rotates.

A starter motor using electricity from a starter battery which is charged from solar energy can be provided on the same axis as the transfer chamber or the moving piston. The starter motor can rotate about the axis and accordingly rotation is started.

charge

Pressure management can be done as follows.

In a motor in which the piston moves, this piston needs to be pressed, and the pressure changes at a transition point where the circumferential length changes from the largest value to the smallest value. This pressure change can be made electronically by computer and jet jet. Because the pressurized fluid needs to be retained, the solution requires a new solution.

New electronic / mechanical solution

Alternatively, since the pressure change has a predetermined frequency, a mechanical solution can be provided. For example, the camshaft communicates with the drive shaft via a time belt. The camshaft can press the flexible membrane in communication with the fluid requiring pressure control.

To make such a solution less complex, the chamber may include, for example, one subchamber instead of four subchambers, so that only one pressure change is required.

In a motor in which the chamber moves, for example, five pistons need to be pressurized, and the pressure changes at a transition point where the circumferential length changes from the largest value to the smallest value. This pressure change can be made electronically by computer and jet jet. Because the pressurized fluid needs to be retained, the solution requires a new solution.

New electronic / mechanical solution

In the motor in which the chamber moves, for example, the internal pressures of the five pistons are different from each other but need to be managed in the same order, and as the pattern repeats at each revolution, the camshaft solution is likewise employed Can: The camshaft communicates with the drive shaft via the time belt. The camshaft can press the flexible membrane in communication with the fluid requiring pressure management per piston.

11F, the < RTI ID = 0.0 >

A more reliable system can be obtained by separating the fluid in the piston and the enclosed space from the fluid in the repressurized phases, in accordance with the new principle according to Figs. 11f and 13f for pressure management. The pressure change in the piston can be obtained by the volume change of the enclosed space of the piston. The reliability can be improved with respect to the reduction in the number of translational movements of the pressurized fluid in which leakage may occur. According to this principle, the control devices can mainly use energy to change the volume of the enclosed space. By using this energy considerably well, it is also possible to use a piston which moves in a sealed state in the cylinder (for example, one piston for the function of the piston and preferably one piston for speed / power - (Such as a separate piston for power management), the cylinders being of different cross sectional areas and, for example, as the circumferential length varies, 65% of the energy used is reduced . Also, in embodiments in accordance with this principle, providing a stationary piston in the interior of the rotating chamber may be the best choice to reduce the use of energy. Although the circumferential length may be constant, the energy reduction efficiency may be lowered in this case.

The pressure change (and consumption) of the fluid inside the expandable piston can also be made in a modified manner, as an alternative to the principle shown in FIG. 11A. By changing the volume of the enclosed space of the piston temporarily, it is possible to change the power (torque) of the motor through the adjustment of the volume, and such changes can be made continuously or simultaneously. Energy is supplied.

A more efficient method for using the effective energy is proposed, and this method can increase the reliability of the motor in connection with the principle as shown in FIG. 11A. According to this new principle, there is no leakage of the high pressure fluid during the movement of the piston from the second longitudinal position to the first longitudinal position, and the piston is connected to the crankshaft-large end bearing, The leakage of the low pressure fluid does not occur during movement from the first longitudinal position to the second longitudinal position in the same joints.

The energy used can be used to move the piston in a conical chamber that can be optimized to reduce the operating force applied to the piston rod of the piston to change the volume of the enclosed space. Also, the energy used can be used in similar piston-chamber combinations, in the same manner as is used for volume control of the enclosed space, for the volume change.

Movement of the piston of varying volume may be accomplished, for example, by the use of valves or other types of control devices or magnetic guides to provide pressurized fluid that moves the piston in one direction from one point to the other, ≪ / RTI > This type of movement is effective in the case of a piston whose volume of the enclosed space is adjustable, and the movement control of the piston can be carried out in a manner that communicates with, for example, a speed control device controlled by a person or a computer.

The motor rotational power supply < RTI ID = 0.0 >

Fluid pressure changes (and consumption) within the expandable piston can also be made in a modified manner, as an alternative to the principle shown in Figure 12a. By changing the volume of the enclosed space of the piston temporarily, it is possible to change the power (torque) of the motor through the adjustment of the volume, and such changes can be made continuously or simultaneously.

According to this principle, the rotational power sources are more efficient than the translational motion power source systems. Since the distance from the first rotation position to the second rotation position has a value of almost zero, a piston which changes the volume of the enclosed space is provided on the cam disk, which can be mounted on a shaft about which the motor power supply source is rotated . In fact, these are the most efficient motors.

The motor with the circular chamber may comprise a wall, at least some of the length * of the centerline of the chamber being parallel to the central axis of the chamber.

For a single motor, the conical chambers (elongated or circular *) may be of a constant type with the force of the piston rods generated by the actuator pistons. Further, such a motor may be a case of any one of the pumps mounted on the motor in which the fluid is pressurized.

The chamber in which the actuator piston is disposed may comprise convexly shaped inner walls of longitudinal cross section sections in the vicinity of the first longitudinal position and the sections may be divided from each other by a common boundary, The distance between the common boundary sections defines the height of the walls of the longitudinal section sections, the heights being reduced as the internal overpressure ratio of the piston increases, or decreasing from the first longitudinal position to the second longitudinal position And the lateral height of the common boundary portions of the cross section can be determined by a maximum operating force that can be selected as a constant value for each of the common boundary portions.

When the piston is disposed in a cylindrical chamber having a tapered inner center, the convex walls have a concave shape.

In addition, the piston-chamber combination may comprise a wall of a cross-sectional boundary parallel to the central axis of the chamber.

In addition, the piston-chamber combination may comprise a transition between the convexly shaped wall and the parallel wall, the transition comprising at least one concave shaped wall which can be arranged in the vicinity of the second longitudinal position .

In addition, the piston-chamber combination may include a concave shaped wall that can be disposed on at least one convexly shaped wall.

The various embodiments described above are given by way of example only and are not to be construed as limiting the invention. It will be apparent to those skilled in the art that various changes, modifications and variations in the components that may be made without departing from the true spirit and scope of the present invention, and not strictly following the preferred embodiments and examples illustrated and described herein ≪ / RTI >

A piston of the type having all piston types, especially those with containers with elastically deformable walls, can be hermetically connected to the chamber wall during movement between the longitudinal positions, May or may not be connected. Alternatively, the piston may be mated and sealed to the wall of the chamber. Also, mismatches between the walls may not be made, and the walls may not contact each other, and such contact may occur, for example, when the container moves from the first longitudinal position to the second longitudinal position within the chamber It can be done in a situation.

The connection of the various types between the walls (the sealed state and / or the mating state and / or the contact state and / or the unconnected state) is determined by the correct internal pressure inside the container wall; Can be achieved by high pressure for sealed connection, low pressure for mated connection and, for example, atmospheric pressure for a disconnected condition (production sized container), so that the container preferably has an enclosed space Since the enclosed space can control the pressure inside the container from the position outside the piston.

Another option for the mating connection is to provide a thin wall to the container which may have stiffeners that protrude from the surface of the wall such that leakage may occur between the walls of the container and the walls of the chamber.

In the case of an actuator piston connected to the main shaft by a crankshaft, there are one or more actuator pistons, all of which are connected to the same main shaft. As an advantage of this configuration, rotation of the main shaft can be performed more smoothly when the longitudinal positions of the actuator pistons are different from each other. Thus, when moving from the second longitudinal position to the first longitudinal position, a "moment of hesitation" may occur at any point in each of the actuator pistons.

All of the actuator pistons are in the chamber from a second longitudinal position to a first longitudinal position and vice versa, either in a mating or sealing state (which, when moving within the chamber, Position, so that in order to synchronize the force of each of the actuator pistons with the main shaft, the piston rod, i.e., the connection from the actuator piston to the crankshaft, The force applied to the rod can be independent of the position of the actuator piston (see the description of "19620 " and the drawing).

The preliminary investigations so far did not quantitatively include the lack of heat generated by the motor of the present invention as compared to the Otto motor type.

The motor of the present invention is still more interesting and persuasive even when heat loss may be involved. For the current Otto motors, efficiency can be 25% due to heat loss. In the first example, assuming that the motors of the present invention generate no heat at all, the fluid is pressurized from 5 bar to 10 bar (10 bar pressure already present in the pressure storage vessel at the time of motor production) Can be reduced by approximately 65%. The total efficiency of the motor according to the present invention is less than 10%, i.e., less than 8.75%, by self-propelled actuator pistons, and this efficiency can be unprecedented up to now (David JC McKay, Environmentally friendly energy). When the pressure regeneration pumps shown in the present invention again use the piston-chamber combination of the types according to the invention, another 65% energy is saved. Thus, ignoring the heat generated by the pump, the total energy usage is 8.75% x 0.875 = 7.6%. However, when some of the energy used for pumping can be supplied from other sources, such as, for example, solar energy (photovoltaic cells), the energy used for regenerative braking devices or flywheels Can be terminated at less than 10%.

19618 - Corrections added to the description 19611 Content - Preliminary investigation

The preliminary investigations so far did not quantitatively include the lack of heat generated by the motor of the present invention as compared to the Otto motor type.

The motor type of the present invention is still more interesting and persuasive even when heat loss may be involved. For the current Otto motors, efficiency can be 25% due to heat loss. In the first example, if it can be assumed that the motors of the above types of the invention do not generate heat at all (isothermal state), the fluid may be fed from 5 bar to 10 bar bar pressure is present), by about 65%. The total efficiency of a motor of the type according to the present invention may be less than 10%, i.e., less than 8.75%, by self-propelled actuator pistons, and this efficiency may be unprecedented until now (David JC McKay Environmentally friendly energy without generating hot air). If the pressure regeneration pumps shown in the present invention again use a piston-chamber combination of the types according to the invention, another 65% of the energy can be saved. As a result, ignoring the heat generated by the pump, the total energy usage may be 8.75% x 0.875 = 7.6%. However, if some of the energy used for pumping is different from other energy sources, such as a battery that is charged by solar energy (photovoltaic cells) and / or a fuel cell (e.g., H ₂ ) , The use energy of the regenerative braking devices or the flywheel coupled to the generator may be less than 10% of the total energy used.

As already concluded at the outset, the configuration of the motor of the type according to Figs. 11f and 13f can be most efficient (simple configuration, almost isothermal thermodynamics) and also most reliable (leak prevention) The crank generating the rotation is not used, and the configuration of Fig. 13F is used for the quantitative evaluation of the motor for the vehicle.

For the current technology of the present invention, VW Golf Mark II model RF (1600 cc), the weight is 836 kg, the 53 kW / 71 pk gasoline motor is used, the diameter is 81 mm and the pressure is 9 bar Lt; RTI ID = 0.0 > 77 mm. ≪ / RTI > In this case, the maximum force per cylinder is 1159 N, which corresponds to approximately 116 kg per cylinder. If all the combustion parts are removed from the vehicle body and the body is made of aluminum rather than steel, it can be assumed that the weight is reduced by about 50%. Therefore, if the passengers are four and carry a load, a force of 58 kg per cylinder may be required to drive the aluminum bodywork.

The maximum operating force of the pump chamber shown in WO 2008/025391 is 260 N (26 kg), with a total stroke of approximately 400 mm and a diameter of 58 mm to 17 mm at a pressure of 2 bar to 10 bar. The use of an expandable ellipsoidal piston in such a chamber results in a substantially good actuator function. Thus, two of the chambers being used as part of the actuator of the current art may be equivalent to one cylinder of the gasoline motor of the VW Golf Mark II, in the case of the VW Golf Mark II being formed of aluminum, All parts have been removed.

In the motor according to the present invention, the pressure of the enclosed space of the actuator piston is approximately 0 bar (stroke: first longitudinal position to second longitudinal direction) at x bar (stroke: second longitudinal position? First longitudinal position) Position). To limit energy usage, the value of "x" can be chosen to be as small as possible. Since the magnitude of the operating force is independent of the pressure value when using the particular type of chamber, it may be possible to limit the pressure using a pressure window in the range of the highest level of 3.5 bar to the lowest level of approximately 0.5 bar.

The starting points may be based on the pressure configuration inside the spherical body piston disposed in the rotary chamber of Figure 13f, but 3½ bar is only the portion of the particular chamber stroke (216.2 mm out of 400 mm) (the force per actuator piston is Up to 260 N), the chamber may be formed in a simpler shape than the chamber shown in FIG. 13F.

The volume change of the spheroid may be quite large: V ₂ = 4/3 x 3.14 x 12.55 ³ (diameter 25.1 mm; P ₂ = 0.35 N / mm ² ) = 8280 mm ³ to V ₁ = 4/3 x 3.14 x 23.45 ³ (diameter 46.9 mm; P ₁ = 0.05 N / mm ² ) = 54015 mm ³ , ΔV = 6.5, ΔP = 7. The angle between the central axis of the chamber and the wall is L ₁ = 302.78-86.57 = 216.21,? R = 10.9: angle = 2.9 ° (these angles are good).

The volume of the actuator piston at the first longitudinal position (index 1) is "virtual" in volume at the second longitudinal position (index 2) with respect to the complete one stroke (L ₁ ) The energy used to compress is W _isotherm = -P ₁ V ₁ ln (P ₂ / P ₁ ) = 0.35 x 54015 x In 7 = 0.35 x 54015 x 2.302585 x log 7 = 36788 Nmm / channel / piston / revolution = 36.8 J / channel / piston / revolution number. The motor according to the invention is not as fast as the gasoline motor (900 revolutions per minute) with respect to the number of strokes per minute, since it is assumed that the expansion and contraction rate of the actuator piston formed of reinforced rubber is slower . Assuming 60 revolutions per minute, it is 1 rotation per second (15x slower than in the combustion motor). W = 36.8 J / channel / piston / second. 2 x 4 'comparable' chambers (cylinders) are provided, the power is 294.3 J / s per piston and is 0.295 kW per piston. If five pistons are used, one is placed in each of the five subchambers of each of the 360 ° channels (FIG. 13F), and the generated power may be 5 x 0.295 kW = 1.47 kW.

Assuming 1 revolution per second, as shown at the beginning of this investigation, the power of the combustion gasoline motor can be saved as 92.4%, 53 kW, so only 7.6%, only 4.03 kW can be used. If the number of revolutions per second is approximately rounded to three revolutions per second, such a motor may first comply with the calculations described above.

Thus, a 2x4 " comparable " chambers, each chamber containing five pistons in five subchambers, are rotated at a rate of about 3 x 1.47 = 4.4 kW (= 180 revolutions per minute) Power, and this power may be sufficient to drive the VW Golf Mark II, which is made of an aluminum body.

As indicated in the literature (David Jaysie McKay's environmentally friendly energy without hot air, 127p, Fig. 20.20 / Fig. 20.21), a small electric vehicle uses approximately 4.8 kW of power for operation, You need batteries, you can drive 77 kilometers with one battery charge, and it takes hours to charge. When the energy source is a battery, such a battery can not be charged during driving of the vehicle. These energy sources are just one option and not a preferred embodiment.

How much energy is needed to pressurize and depressurize the actuator pistons and can this depressurization and pressurization be achieved during vehicle operation?

The actuator pistons of the pressurized motor need to achieve a pressure change. The principles shown in Figs. 11F and 13F are used.

The energy can be obtained, for example, from the kinetic energy provided in the rotating chambers in which a piston of a classical piston-chamber combination is moved by a camshaft in communication with the main motor shaft of the motor. When using the data used to calculate the motor power, the pressure change of the inflatable spherical body piston can be made by changing the volume of the enclosed space of the actuator piston by changing the volume of the 'below' classical piston.

In order for the actuator piston to move from the second longitudinal position to the first longitudinal position, a change in the volume of the piston per stroke is required, so that the piston is in the form of a small spherical body with an intermediate internal pressure (3.5 bar) (46.9 mm in diameter) having a low pressure (0.5 bar) to a large volume (46.9 mm in diameter). In this case, the volume of the enclosed space is kept constant by changing the internal pressure of the actuator piston. Regardless of the internal force, the force is 260 N per stroke of the piston, so that if there are eight chambers each containing five pistons and the number of revolutions per second is 3, the generated power is 4.4 kW.

The energy required to reach the second longitudinal position from the first longitudinal position (Figs. 14A and 14B)

1. The shape of the actuator piston (diameter 46.9 mm: 0.5 bar) in the form of production (diameter 25.1 mm: 0 bar (overpressure)) in such a way that the actuator piston is contracted into the volume- ). If the frictional force between the pump piston and the wall of the containment space is small enough, the energy cost can be neglected at all.

2. Energy is required to inflate a sphere (diameter 25.1 mm, 0 bar) to a sphere (diameter 25.1 mm, 3.5 bar) by reducing the volume of the enclosure space where the pump piston moves closer to the actuator piston:

W _isotherm = -P ₁ V ₁ ln (P ₂ / P ₁ ) = -1 (confirmed) x 4/3 x 3.14 x 12.55 ³ x In 4.5 * / 1 = -1 x 8280 x 2.302585 x log 4.5 = 12454 For a 2 x 4 chamber, five actuator pistons are provided per chamber and the number of revolutions per second is 3 = 12.5 x 8 x 5 x 3 Js = 1.5 kW (* P ₁ = Nmm / channel / piston / For an absolute pressure of 1 bar, the P ₂ absolute pressure is 4.5 bar).

Thus, the total generated power is 4.4 kW and the power required to achieve motor operation is at least 1.5 kW, thus requiring approximately 2 kW in addition to the other final losses.

To access the motor, the pump is compared to the effective pump if a pump meeting the above needs to be present in the vehicle. Compressors of the current technology are 220 V, 170 l / min, 2.2 kW, 8 bar, Bessel has a specification of 100 liters. Power is needed, but because it is low pressure, this retrofit compressor will charge the pressure storage vessel somewhat faster.

Since P = 2200 W at 8 bar, a pressure of 3½ bar may be required when using the same repressurization time as at 8 bar, so the required power is 3/8 x 2200 = 825 W. Even if the battery is a 24 V battery, the current is 825/24 = 34.4 A, which is a considerable amount for one battery and consequently the pump, indicated at 826/831, A plurality of batteries are available in the motor configurations shown in Figs. 11A, 11B, 11G, and 12A and 13A. These batteries may be chargeable only by an external power source, so they are inefficient for vehicles for extended periods of use and therefore the capacitor solution (Figure 15e) is still in the study stage. This is not a preferred embodiment and is only an option.

It may be better to prevent power conversion, and it is also advantageous if the pump 826/831 is operated by combustion, for example using H ₂ , which is preferably generated by electrolysis and is selectively generated by the fuel cell It may be better to use the motor configuration of Fig. 15C in communication with the shaft of the motor. The process described above uses electricity from a battery that is charged by an alternator in communication with the shaft as a power source.

It is necessary to generate 825 W of power by the combustion motor, which is a classic 24 cc / 66 cc motor using an Otto cycle which can be compared to currently used large moped motors (The VW Golf Mark II has 53 kW, 1600 cc, 90 mm diameter, 4-cylinder type motors and 825 W corresponds to one cylinder of approximately 24 cc and 90 mm, or 3x faster 2.2 kW corresponds to one cylinder of approximately 66 cc, 90 mm). Mopeds have been on television a couple of months ago, using electrolysis of water stored in tanks (originally a gasoline tank) and using H ₂ generated for the combustion process - these mopeds are feasible. In the case of vehicles, this size of external motor, indeed an auxiliary motor, is used, and all the extra combustion equipment that has been removed from the VW Golf Mark II to reduce weight is regrettably a necessary tool to prevent pollution or CO ₂ emissions Noise can be successfully reduced by appropriate noise reduction measurements, and the weight of the motor is only 15 liters (= 15 kg) of water tank and only 1 of the weight of the vehicle / 6 (= approx. 35 kg) - the feasibility study of these motors may still be in progress.

The motor based on the crankshaft solution (Figs. 11A to 11D and 11F) using the pistons connected to the crankshaft by the elongated chamber and the piston rod / connecting rod is preferably of the same construction as the vehicle And can be used as the main motor of the vehicle. The wheels or propellers may be connected to the central main motor by a distribution device such as a cardan and a drive shaft. Optionally, the motor may be of the type used as a separate motor and may be directly connected to each of the propulsion devices, such as wheels or propellers.

The piston-based motor, which is located around the center of rotation axis and whose size increases and decreases (Figs. 12a-12c, 13a-13g), is preferably controlled by, for example, And can be used as a motor to be disposed. The motors may each be connected directly to each of the propulsion devices. Optionally, it can be connected to the propulsion devices by drive shafts, as a central motor.

The control of the motors may preferably be done by a computer, particularly when each motor is directly connected to one of the one or more propulsion devices used in the vehicle.

The flywheel can be connected to the main central motor, preferably, separately, and separately disposed in each of the propulsion devices. The flywheel can be used to smoothly maintain motion as a classic solution, or it can be used to restore energy for acceleration after braking (and simultaneously storing dynamic braking energy) of the vehicle, (E. G., Figs. 11A, 11B, 11C, 11F, 12A, 12C, 13A, 13B, 13e, and 13f (818, 821, 821 ', 826, 826' in FIG. 13f). Some or all of these types of flywheels may be present in a transport vehicle comprising a motor according to the present invention.

According to another aspect of the recovery energy during braking, the pumps can be connected directly to the main shaft and the central drive shaft (e.g., 821, 821 ') pumps the fluid to a significantly higher pressure, The high pressure fluid can be communicated with the pressure storage vessels (e.g., 814, 839, 890, 889).

In 19617 - 19618 For actuator Of the chambers  Optimal configuration

The geometry of the chambers used optimally in combination with the actuator pistons may differ from chamber to chamber for optimal use of the pump, as the conditions for use with the actuator and the pump may be different.

For example, an actuator piston must provide maximum power using as little energy as possible while moving at a reasonable speed. Further, in the case of an actuator piston in communication with the crank, the subordinate conditions may differ, for example, under conditions of the actuator piston in communication with the rotary chamber, such as when a maximum force is required.

In order to use the actuator piston as a self-propelled piston, it must be a three-chambered chamber of the type in which the wall of the chamber widens outward as it moves from the second longitudinal position to the first longitudinal position. Thus, the angle of the wall with respect to the central axis of the chamber from the second longitudinal position to the first longitudinal position should be a positive value. According to this angle, the speed of the actuator piston can be fixed. Of course, the transition from one point of the wall to another point in the longitudinal direction needs to be smoothed to limit the friction between the actuator piston and the wall of the chamber.

In order to be able to apply a load to the walls of the chamber, the inflatable actuator piston itself requires an internal pressure. In order to allow the actuator piston to move, the center of the flexible wall should be positioned closer to the first longitudinal position than the circumferential surface connected in mating with the wall of the elongate chamber. The larger the distance, the faster the speed of the actuator piston in the chamber.

The reaction force of the chamber wall applied on the actuator piston is such that the piston is pushed out of the wall of the chamber in the first longitudinal direction position with a fixed force. Thus, at least one cap of an actuator piston located closest to the second longitudinal position is assembled to the piston rod by a force applied on the piston rod.

The chamber shown in section 19620 of the present patent application (for example, FIG. 21a), when used in a pump, has an operating force applied to the piston rod at a pressure of 8 bar to 10 bar of an excellent pumping fluid for pumping purposes of approximately 65 %. This reduction should be seen in comparison with the force required in a straight cylinder, and the classic high pressure bicycle pump and chamber can be seen by comparing the progressive bicycle pump with the shape of FIG. 21a. The maximum force of the chamber is substantially independent of the pressure of the fluid inside the chamber and is therefore approximately constant during the pumping stroke (e.g., 2 bar when maximum force is achieved).

The same chamber used in an actuator including an actuator piston may have the advantage that the force is approximately constant during the stroke from the second longitudinal position to the first longitudinal position - the same diameter (same comparison object as described above) The operating force at the price to be paid in connection with the operating force when the maximum pressure is achieved in a linear cylinder having only one third may be about one third. Operating forces of this magnitude may not be appropriate for the purposes of an actuator piston, but may also be inappropriate for a particular force in relation to the use of the crank.

The same principle may be valid even if the chamber is of the elongated alternating ("circular") type. In a particular solution in which the actuator piston does not move and is placed in the rotary transfer chamber, a chamber of the type described above may be used. If more than one piston is used, more than this chamber, for example, five pistons (e.g., Figure 10b) may be needed. If each piston is at a location on a different circular path within each sub-chamber and therefore under different pressure conditions, the force derived by each piston may be the same for all pistons, Nor does it act to push out the other pistons. The total force is 5x when only one piston is used. Depending on the application, gears may be required to achieve the required torque and speed.

Other suitable configurations for the actuator chambers may be possible.

The parameters of the elongated chamber with the actuator piston connected to the crank may be as follows:

The length L of the chamber is relatively short, a relatively short stroke length is obtained,

The force F (p, d, mu) may change during the stroke from the second longitudinal position to the first longitudinal position so that when the actuator piston reaches the limit of the first longitudinal positions, Where p is the pressure inside the actuator piston, d is the diameter of the chamber at a given longitudinal position, and mu is the distance between the wall of the chamber and the flexible wall of the actuator piston, where F is the force exerted from the piston rod, p is the pressure inside the actuator piston, .

The frictional force F ([mu]) during the entire return stroke is achieved by a slight suction of the overpressure of the actuator piston at zero [F (mu) is the coefficient of friction between the chamber wall and the flexible wall of the actuator piston).

The velocity v (φ, F) should be optimized for the length L of the chamber, where v is the relative velocity of the actuator to the chamber and φ is the distance between the wall of the chamber and the central axis of the chamber Angle, and F is the force applied from the piston rod.

The energy used is as small as possible - thus the pressure drop when the actuator piston moves from the second longitudinal position to the first longitudinal position while the volume of the piston changes while the enclosed space is temporarily closed ( ΔV) should be as small as possible.

21A having a pivotal cross section and having a wall disposed about a pivot axis, the center being disposed at the center of the main motor shaft and being rotatable, and one or more actuator pistons being movable in a non- The parameters of the chamber, which are arranged and mate with the chamber wall are as follows:

Regardless of the distance to the center of rotation, the circumferential length of the chamber wall must be the same, which can affect the shape of the cross-section of the chamber.

• The coefficient of friction must have an optimum small value using improved lubricants, such as super lubricants, that function well with metals and rubbers, such as steel or aluminum, with a significantly lower coefficient of friction than other lubricants.

However, it may be necessary to achieve the effect that the circumferential length of the chamber wall should be the same, irrespective of the distance to the rotation center, as well as the piston production of the optimal configuration may be required. Regardless of the distance to the center of rotation, the circumferential surface of the chamber wall should be the same.

Thermodynamic Issues in 19617 - 19618

System (chambers with elongated chambers with actuator pistons in communication with the crankshaft, chambers may be arranged symmetrically about the pivot axis and may communicate with the crankshaft or the main shaft of the motor) , The heat can be generated fairly well.

A pressure storage vessel in which fluid is stored may be arranged during production of the device in which the motor is being used. During operation of the motor, a small amount of heat may be generated in the storage vessel and higher pressure fluid from the last pump of the pressurized cascade flows into the fluid of the vessel, which may have lower pressure (Figures 11 11c, 12a-12c, 13a and 13b).

In the first pump of the pressurized cascade which is capable of receiving energy from the main shaft by the pressure of the fluid entering from the third enclosed space of a motor of the type using a crank assembled in the main shaft of the motor, And generates heat. In addition, it is also possible to use other energy source (s) (preferably solar cells, fuel cells, environmentally friendly energy source (s) such as electric batteries), or alternatively a generator in communication with the internal combustion engine A different portion of the heat of approximately the same size may be generated by a pump capable of receiving energy from a classical energy source (e.g., a classical energy source, such as an electric battery being charged by the heat source) (Figs. 11A to 11C, 12A).

In the actuator piston, the pressure in the cavity + enclosed space inside the actuator piston body from the second enclosed space and the expansion into the third enclosed space occur. As this pressure action can be made somewhat better than the expansion, the actuator piston can exhibit a temperature higher than the temperature at the start of the motor (Figs. 11A to 11C, 11F, 12A to 12C, 13A to 13E ).

Thus, such a system generates heat which can be used, for example, for heating of a vehicle compartment or can be used to heat a third enclosure space where expansion (insulation) takes place. Since such a system is disposed inside the crankshaft, heat generation is not easy. Thus, this action can be made in a substantially non-thermal situation.

Of course, it may be desirable to compensate for heat generation in isothermal conditions. When the pressure change inside the actuator piston is controlled by the piston moving inside the chamber of the bidirectional pump (in fact, the enclosed space of the actuator piston), the compression and pressurizing action occurs inside the chamber in such a way that the volume is changed So that the heat generation and the cooling operation can be balanced. This may correspond to a combination of a non-removable actuator piston and a moveable (rotatable) chamber (Figures 13f-13g). Also, for thermodynamic aspects, this is the most efficient motor principle since (theoretically) efficiency can be nearly 100%.

19617 - Correcting to work with motors at 19618/19627 19615 Energy sources

The motor can operate with other energy sources, which are preferably environmentally friendly, and optionally not environmentally friendly. This energy source may need to supply about 7.5% of the motor, for example, to limit the efficiency improvement with respect to the classical motor burning fossil fuels using an Otto cycle.

For example, an environmentally friendly energy source, such as latent energy from the sun, hydraulic and wave power and other sources, does not result in the release of undesirable chemicals such as CO, CO ₂ , NO, etc. when energy is generated .

In the case of a motor according to the present invention, the energy source (s) preferably comprises, for example, electricity, a capacitor (= electricity stored in a fairly large capacitor) or, for example, Or may be electric batteries of the type that are charged by solar cells through non-equipped photovoltaic solar cells or by H ₂ or air that is compressed by, for example, potential hydraulic energy, or the like. H ₂ Fuel cells can be 'charged' by H ₂ , which can be derived from the electrolysis of H ₂ O, which can be stored in the vessel, and this electricity can be supplied from a special battery that can provide energy continuously (no starting battery) Can be supplied. Such a battery may be charged by an alternator and / or photovoltaic solar cells in communication with the axis of the motor. H ₂ can also be stored in a special vessel and can be inserted directly into the fuel cell.

The optional energy sources may be electricity, and may be capacitors or electric batteries of the type that are charged by an electric generator driven by a motor driven by a fossil fuel or the like, or by a rotating electric generator based on steam generated by a fossil fuel- have.

The motor according to the present invention may comprise one energy source, or a combination of energy sources, which is preferably environmentally friendly, optionally environmentally friendly and not environmentally friendly.

When the motor is used as a motor of a transport device, such as ships, trains, cars or airplanes, whose ability to connect to large energy sources is limited, the batteries may be connected to an external energy source As shown in Fig. Charging of other energy-containing materials, such as H ₂ , may be accomplished by hoses or the like. Thus, the energy containing material disposed in the apparatus is charged by means suitable for temporarily connecting to the external energy source (s).

The devices may be desirable to be able to travel across a self-supported strategic distance, without prolonged charging of external energy from an external effective power source (e.g., electricity). Strategic distances can be defined in many ways. For example, in the case of a commuter vehicle, a commutation distance of 2 x 50 km per day and an arbitrary distance of 40 km may be sufficient without recharging, for example, in the case of a vehicle used for longer distances, km, or may even have to travel at twice the distance. The above-mentioned distance may be a limit value of a distance that a person has to carry out in one day.

Preferably, the power of the mobile device (e.g., a battery, a fuel cell, the electrolysis of H ₂ O resulting from H ₂ effective for combustion applications, a pressurized fluid, or other Other possibilities) can be supported on their own for at least one day. Preferably, it can also travel at night. Preferably, the power source may not be critical in terms of efficiency, but may not add significantly to the extra dead weight (which increases the RAT), which is particularly important for vehicles.

There are many types of batteries, and the latest batteries are high-powered, efficient, and do not add a lot of deadweight and dead space. Although charging these batteries takes a lot of time and requires infrastructure, the rapid charging of the batteries is not impossible and can not distinguish between new and old batteries. The charging of the solar cell may not be sufficient for the use of energy (see preliminary investigation). It is necessary to provide connections and plugs to the electricity supply network as an effective infrastructure.

In order to shorten the charging time from one minute to two minutes, the 'battery' based on the suitcase-sized condenser charge and the electric discharge control to the motor system is a fairly good solution to all of the above- Lt; / RTI > This is being developed in the USA.

Fuel cells are costly and can be considerably less efficient in terms of generating electricity, but they can solve the problem of adding weight to a significant degree and are free of noise. These fuel cells are contrary to the traditional way that combustion (fossil) motors communicate with alternators. For example, H ₂ is a safety hazard and storage of H ₂ may be difficult due to leaks from the vessel (which does not cause leakage problems in relation to other materials). In addition, although residential electrolysis systems are already on the market, distribution infrastructure may be needed because these electrolysis technologies can only produce H ₂ for self-use. However, after a moped with a combustion motor (<50 cc) using H ₂ obtained by instant electrolysis of water (usually stored in a tank where gasoline has been stored) in 2009, It may be possible to use such a moped technique. Electricity for electrolysis can be supplied from a battery that is designed for use in equipment (continued use) and can be charged by an alternator using the dynamic rotational energy obtained from the motor, and such electricity can be supplied, for example, It is also charged by the battery.

For example, electricity generated by a fuel cell using H ₂ may be used to charge the battery, and generated electricity of the battery may be used for motor functions. An alternator may be in communication with the main shaft of the motor and may also charge a battery, e.g., the continuous-use battery, and a starter motor battery possible with current technology for a starter motor available in the state of the art. Solar cells may be added to charge the batteries. For example, electricity generated by a fuel cell using H ₂ may be directly connected to motor functions that bypass the battery (s).

As another possibility, for example, H ₂ may be used for combustion, for example, the motor may comprise a classical piston-linear cylinder combination with a crankshaft, wherein the crankshaft is charged And serves to rotate a shaft that communicates with the alternator used for the operation. The alternator may also be directly connected using wires to other motor functions. The power of the combustion motor can meet the power supplement requirement that the motor according to the present invention can not generate. The power of the combustion motor can be significantly less when compared to that of combustion motors of the prior art when used 100% in the motor functions. Thus, for example, the configuration necessary for the electrolysis process to produce H ₂ can be movable, for example, for use in a vehicle.

For example, a bi-directional pump that changes the volume of the enclosed space of the non-movable piston disposed in the rotary chamber may be required in the present invention, such as, for example, an electric motor in which the piston rod of the pump is assembled If it can be used to rotate about an axis in communication with the crank, it may require electricity. The axis may be, for example, the main axis of the combustion motor using H ₂ as fuel.

In another configuration in which the pump is used for repressurizing the fluid and the fluid is used to control the actuator that controls the pump, this configuration may have the same configuration as the entire solution described above.

Other configurations may be used that do not use electricity to change the volume of the enclosure space when the pump is replaced with a camshaft. Electricity may be required only for the starter motor, and may be supplied from an alternator driven by the main shaft of the motor and / or from a starter battery which may be charged by solar cells. The camshaft solution may preferably use one or more pistons, optionally a single piston. A small pump may be required by the electric motor supplied with energy from a battery designed for continued use or for acceleration which means higher pressure of the actuator piston driven by the main shaft.

A tank containing conductive water can be charged from an external water reservoir, and if the water is nonconductive, water can be made conductive by adding a conductive material.

The pressure storage vessel may be pressurized (not shown) by a pluggable connection, not only by the pump of the cascade arrangement, but also optionally by an external pressure source (2701 of the drawings).

The battery may be charged by an alternator, solar cells, and / or H ₂ fuel cell as well as optionally an external power source through a pluggable connection (reference numeral 2700 in the individual drawings).

Both the piston and the chamber can be rotated about an intermediate point that is the center of rotation of the chamber.

The present invention can be constructed with a lower weight than that based on classical piston-cylinder assemblies.

Since the motor can function in the dark, supplementation or addition of solar cells may be necessary. For example, a H ₂ type of fuel cell, for example a fuel cell, may be needed which reacts with other environmentally friendly power sources, for example, O _{2 in the} atmosphere to provide electricity and H ₂ O. Such a fuel cell may require a relatively small storage vessel that may have a reduced pressure. In other words, the H ₂ distribution system may be residential, or the distribution density of the distribution system may not be high.

In a motor of the type in which the containment space communicates with the recoil cascade pumps, electricity can be used to provide energy to the electric motor driving the piston pump through the other crankshaft. The use of such electricity can be done, for example, as a supplement to the energy of the solar cells in the dark case, or such electricity can be used at any time.

Further, a generator capable of being driven by the main shaft and capable of charging the battery can be added to this type of motor.

In motors of the type in which the fluid in the containment space is separated from the re-pressurized cascade, possible ore electrical energy may be required for control of the valves. Accordingly, other environmentally friendly power sources, such as the fuel cells described above, may be needed, rather than more environmentally friendly solar energy.

Also, electrical energy may be used in the external cascade system, which is not added to Figures 11f and 13f, and may be required for the repressurization of the pressure vessels 1063 and 889. [ The use of such electrical energy may be accomplished by pumps of the cascade arrangement comprising at least one pump in communication with the main shaft and at least one pump in communication with the external power supply. The pumps can communicate with the pressure vessel. In the case of the solution of Figure 13f, one pump may be sufficient.

Transmission-clutch at 19617 - 19618

The motor according to the invention is characterized in that when the piston is operated in the elongated chamber or when it is operated with its position changing from the first position to the second position of the circular path in the circular chamber, (Rpm) that is limited by the shape and / or pressure variations in the longitudinal axis (e.g., longitudinal positions). For example, the flexibility of an inflatable piston having a wall and a reinforcing layer formed of rubber and thus capable of having the hardness of the rubber, how many reinforcing layers are used, and the angle between the reinforcing layers if more than one layer is used Is the key (see 19650 ).

The motor according to the present invention is a two-stroke motor in which the piston is operated in a three-chambered chamber, performing one half turn during the power application stroke and half rotation during the return stroke. Compared with the preliminary investigation of a 4-stroke 4-cylinder 1595 cc VW Golf Mark II petrol motor with an idling speed of 700-800 rpm and a maximum speed of 2500 rpm (OK) , The comparable speed of the motor according to the present invention may be half the speed described above. This reduced speed is suitable for the motor according to the invention.

When the clutch is started to match the flywheel, the impact applied to the main motor shaft by the reduced speed is limited. In the preliminary investigation, the motor configuration has been considered in the case of having a comparable torque per kg of the weight of the vehicle in relation to the aforementioned Golf Mark II. As long as this configuration is maintained, the total weight of the vehicle according to the present invention is reduced by 50% Can not be considered.

If a transmission (manual, automatic - for example, Van Doorne's Variomatic (belt-drive automatic transmission) or an ordinary fluid-operated automatic transmission) is used, the gear ratio and the number of gears It can be different from the vehicle being used. The special features of the combustion motor (limitation of the function window in terms of the rpm of the main motor shaft) not existing as the main part of the motor according to the present invention have not been described above. As described above, when a transmission is required, an automatic transmission, optionally a manual transmission, is provided.

The following can be considered quantitatively:

- Wheel diameter: 0.65 m (VW Golf Mark II),

- Motor idling speed: 350-400 rpm - Motor driving speed: 2x idling speed

therefore,

60 km / h: Motor: 750 rpm

          Wheels: 490 rpm, thus: gear ratio: less than 1: 1.5

90 km / h: Motor: 1000 rpm

          Wheels: 735 rpm, thus: gear ratio: 1: less than 1.35

120 km / h: Motor: 1250 rpm

          Wheels: 980 rpm, thus: gear ratio: less than 1: 1.28

140 km / h: Motor: 1500 rpm

Wheel: 1143 rpm, thus: Gear ratio: 1: Less than 1.31

conclusion

● If reverse traction is required, a transmission may not be necessary and another weight reduction may be obtained.

• The RPM is still too high for the shape change of the swinging piston and, once proven correct, a transmission may be required. If so, a relatively slow rotation motor may be needed to increase the rpm, and in order to be able to use the acquired rpm for the wheels of normal size, in order to be able to couple the motor to the wheels by the clutch, can do.

Motor sound at 19617 - 19618

The pitch of the sound of the powered parts of the motor according to the present invention is considerably smaller due to the lack of explosion and can be significantly different from the commonly known engine sound of gasoline motors based on the Otto motor design Quot; Why engines sound so good "of the prior art, No. 402, No. 86-89, of Classiccars. Instead, a sound may be produced due to friction between the chamber and the metal or plastic inflatable rubber piston body (e.g., super lubricant), which may be low frequency.

In the elongated chamber design only the frequencies of the pitches of sound (from the second longitudinal position to the first longitudinal position) / silence (from the first longitudinal position to the second longitudinal position) are shown, Sound is generated continuously - both chambers are fricative, and such fricatives can be at low frequencies.

In order to achieve the same or comparable power, since the motor according to the present invention is a two-stroke motor (note: green motor!), While most of today's motor vehicles are four-stroke motors, Can be half in the motor according to the Otto design. Also, in such a motor, the number of revolutions per minute that can add a low frequency sound is lowered.

It also makes noise from the pump (compressor), which creates the pressure for repressurization of the pressure vessel. If the pump is a piston-chamber type according to the invention, according to the re-pressurized type motor according to the drawing, noise may occur to some extent from the valve, noise may be generated as the fluid is directed from the chamber to the pressure vessel, Noise may also be generated when the reduced-pressure fluid is introduced.

Air compressors of the prior art, based on pistons moving in a tandem chamber, make absolutely no sound. These sounds can be attributed to the fact that the air movement speed can exceed the speed of sound and shock waves cause extreme noise.

In the design according to the invention, it is preferred that the velocity of the fluid be lower than the sonic speed and, optionally, the shock wave from the air movement velocity excess wave is buffered, for example by opposing wave designs Even the motor is a combustion motor type, as in Audi vehicles.

No valves are provided in the repressurizing motor of the type according to the drawings, and only extra piston chamber assemblies are provided to induce a pressure change. This type of motor is also the most efficient and also the quietest motor of all types according to the invention.

Approximately 60 cc of Otto motors (comparable to moped motors) may be required to generate power to (re) charge the batteries to power the pumps (see preliminary investigation). Here, the pump can re-pressurize the pressure vessel that can provide pressure for the main motor component, which preferably uses H ₂ as the working fluid, optionally gasoline / diesel or other combustion fluid . The sound of these moped motors is usually severe, but may be acceptable if sufficient noise absorption is achieved.

Therefore, in the motor according to the present invention, no sound can be generated at all as in the electric motor, but a low-frequency sound with a small pitch is generated. Accordingly, from the viewpoints as can be confirmed through sound, the vehicle corresponding to the foregoing is superior to the vehicle having only the electric motor that operates at low speed.

The low frequency can be changed if the low frequency is judged from the working prototype.

19627

In a first aspect, the present invention relates to a combination of a piston and a chamber,

The chamber includes a wall of a cross-sectional border parallel to the central axis of the chamber.

Wherein the chamber comprises a second chamber communicating with the first chamber through a channel, the channel comprising a longitudinal section section provided with a concave shaped wall, the wall of the second chamber defining a center of the chamber Parallel to the axis.]

For example, a conical chamber of a progressive bicycle pump may be divided into longitudinal cross-section sections, and the common boundaries of these sections may include, for example, a piston in the first longitudinal position of the chamber and a second longitudinal direction (For example, pressure above atmospheric pressure) grade such as 1 bar, 2 bar, ..., 10 bar that can be generated while moving to a position. The chambers comprising longitudinal cross-sectional sections of convex and concave shape, the sections being separated from each other by common boundaries, the height of the walls of the longitudinal section sections thus obtained decreasing with increasing overpressure ratio, The lateral lengths of the cross-sectional boundaries of the cross-sections are determined by the maximum operating force. The maximum operating force of the common boundary portions is selected to be a constant value at least in the vicinity of the second longitudinal position.

As another factor for determining the appropriate longitudinal cross-sectional shape of the chamber in relation to the proper sealing of the chamber wall and piston at the bottom position of the piston (second position), for example, the chamber is designed to lower the operating force (For example, in WO 2008/025391, the diameter of the smallest part of the chamber was 17 mm) at the point where the pressure is highest So that a sufficient space can be provided for moving it.

The longitudinal cross-section sections may have convex and / or concave sides. In order to keep the convex / concave portion of the chamber at a predetermined ergonomic height so that the user can perform the pumping operation more comfortably, in the configuration used in the bicycle bottom pump, the start portion of the chamber has a convex- And a concave wall portion, the beginning of which coincides with the conical bottom (WO 2008/025391).

A spring force-actuated piston, for example a flexible, inflatable, inflatable container piston (e. G., EP 1 384 004 B1) is adapted to move from a second longitudinal position of the chamber to a first longitudinal position, You can start moving. If the sealing pressure is applied to the convex / concave chamber walls from the piston and the longitudinal component of the frictional force between the piston and the chamber wall is lower than the longitudinal component of the sealing force, the cross sectional area and circumferential length of the second longitudinal position Sectional area and circumferential length of the first longitudinal position. For example, in order for the piston to be held in a position controlled by the user of the bicycle pump, the wall of the chamber in contact with the piston may have to be parallel to the central axis of the chamber. This parallelism provides a sealing force with no longitudinal component, thereby ensuring that the piston remains sealed in the wall of the chamber only at a desired position of the user. For example, in the case of the chambers shown in EP 1 179 140 B1, a part of the inner wall of the chamber at the top (first longitudinal positions) and bottom (second longitudinal positions) The piston rod is displaced in the above-mentioned position if the pump is not in use or the piston rod is changed in the upper part of the chamber by the user when the pump is in use. EP 1 179 140 B1 does not disclose the reason for the parallelism.

In the case of a piston of this type, the movement from the second longitudinal position to the first longitudinal position in the chamber may be performed when the piston is moveable in a mating state in the chamber or when the piston is movable in a sealed state If possible.

In a second aspect, the present invention relates to a combination of a piston and a chamber,

The chamber has an outlet between the convex wall and the concave wall,

The outlet communicates with the hose.

The longitudinal cross-section sections may have convex and / or concave sides. In order to keep the convex / concave portion of the chamber at a predetermined ergonomic height so that the user can perform the pumping operation more comfortably, the bicycle bottom pump is provided with a chamber having a convex end portion and a concave wall portion And this starting portion can coincide with the bottom of the conical shape (WO 2008/025391).

If the bottom portion is hollow, the bottom portion can be used in three ways.

According to one exemplary embodiment, an outlet is added at the second longitudinal position of the chamber while keeping the portion open. The outlet may preferably be in direct communication with the hose.

Optionally, the outlet comprises a check valve, which communicates with an expansion chamber which is built into the bottom of the chamber. In this case, since the volume of the expansion chamber is caused to expand irrespective of the pressure, there is a problem that such an expansion chamber may be required only at relatively high pressures, and at low pressures, the speed of the pump is delayed. This solution may be necessary if the piston is caught in a concave shaped transition from convexly shaped wall portions to another longitudinal position of the chamber, or if the piston is too large to move to another longitudinal position.

In a third aspect, the present invention relates to a combination of a piston and a chamber,

At least the concave shaped inner walls are disposed between the two common boundary portions.

Preferably, the hollow portion may be used as an additional pumping volume of the chamber, and the piston must be able to move toward and away from the bottom without pinching. A smooth transition is required extending from the wall of the convex shape of the cross-sectional sections, said transition comprising a wall of concave shape. Depending on the height of the cross-sectional sections, and hence the pressure ratio, these concave shaped walls can be arranged at least between two or more common boundaries at the above-mentioned high pressures.

If there is not enough space around the second longitudinal position where the piston is to be moved, there must be enough space to allow the piston to be placed and moved in that position.

In a third aspect, the present invention relates to a combination of a piston and a chamber,

The second chamber includes a third chamber, and the third chamber communicates with the second chamber through a check valve.

Thus, a point on the wall of the chamber may be opposed to the first longitudinal position, the convex shape of the sides of the longitudinal cross-sectional area must transition to the bottom portion of the chamber, and the wall of the chamber is parallel to the central axis . In order to facilitate such a transition, the transition from the convex shape to the concave shape is required, so that the lateral shape of the longitudinal section in the transition portion is shifted from the first longitudinal position to the second longitudinal position It should be concave.

If the sealing, which is incompatible with the transition from the convexly shaped sides of the longitudinal cross section to the concave shape, is achieved over a given longitudinal length, according to one solution, the chamber is closed and closed by a non- The outlet may be formed and the remainder of the chamber may be used as the expansion vessel. This may be useful for proper pumping at high pressures.

In both cases (when used as a large expansion vessel when the bottom portion is used as an additional pumping space), the positions of the common interfaces are at different distances from the first longitudinal position, and the distances between the positions of the common interfaces It is different. The stroke volume of the pump having the expansion vessel is smaller than the stroke volume of the pump using the bottom as a part of the stroke volume.

In a fourth aspect, the present invention relates to a combination of a piston and a chamber,

The chamber is raised by a fourth chamber that is open, and the chamber has an outlet that terminates in the fourth chamber.

The fourth chamber is merely a basic chamber of a specific shape and has no further significance. The chamber may have an exit in the form of a nipple.

In a fifth aspect, the present invention relates to a combination of a piston and a chamber,

The outlet communicates with the hose.

To optimize the pumping speed, the hose of the bicycle pump may be inflatable under a predetermined pressure to form an expansion vessel. This means that the pump performs the pumping action quite efficiently at low pressures, and the hose does not create an expansion vessel, which creates a larger pumping volume than the volume of a single vessel type. Most of the pumping action is done in a low pressure mode. The expansion of the hose can be limited by the reinforcement of the hose, and the expansion can be done only in a part of the hose.

The piston may be movable relative to the chamber wall in a mating state.

The piston may be resiliently moveable relative to the chamber wall.

Additions to the description of 19616 through 19627 to 19620

Using the chamber shown in FIG. 21A, which is used in the advanced bicycle pump, the amount of energy used can be reduced by about 65% at a pressure of 8-10 bar, with respect to the high pressure bicycle pump of the state of the art. The result of this calculation is as follows:

The chamber of Figure 21a has been designed to be at a certain pressure, especially at high pressures, and thus also at a maximum force of 260 N at 8 bar or 10 bar.

The present high-pressure pump includes a linear cylinder with an internal diameter of 27 mm and has a working force at 8 bar of F = px O = 0.8 x 0.25 x 3.14 x 27 ² = 458 N and an operating force of 572 N at 10 bar do.

The reduction at 8 bar is 458-260 / 458 = 198/458, with a reduction rate of 43% and 54% at 10 bar. At 12 bar, the reduction rate is 60% at 687-272 * / 687, while 801-318 ** / 801 = 66% at 14 bar and 916-363 '' / 916 = 60.3% at 16 bar.

The efficiency of the progressive bicycle pump is significantly higher than that of the current high pressure bicycle pump and influences the selection of the maximum force to 260 N. [ However, if a linear cylinder portion of 17 mm diameter is used, the force (F) at a pressure of 12 bar in relation to the conical portion of the chamber should be 1.2 x 0.25 x 3.14 x 17 ² = 272 N *, the force F at 14 bar is 318 N **, and the force F at 16 bar is 363 N ***.

Conclusion : 65% at the proven 8-10 bar had to be 54%. However, as the maximum force F of the selected 260 N affects these results, it can now be good for recalculation of chambers, especially those used in motors but optimized for bicycle pumps.

19617 - 19620 at 19627 Three  Conical chamber  Added to design

The chambers of FIGS. 21A, 21B and 22 to 25 of EP Patent Application No. 1 007 540 27 (September 8, 2010) have been designed with the following mathematical considerations in mind.

The shape of the elongated conical chamber of the pump having the central axis connects predetermined dots (x-coordinate: along the central axis, y-coordinate: perpendicular to the central axis) outside the central axis . The chamber has different cross-sectional areas and has first and second longitudinal positions through which the piston moves between, and the cross-sectional area at the first longitudinal position is greater than the cross-sectional area at the second longitudinal position. Wherein the piston is hermetically connected to a wall of the chamber and wherein a production size of the chamber corresponds to a circumferential length of the second longitudinal position and the shape of the chamber causes the piston to have a predetermined pre- . The position of the dots relative to the central axis is determined as follows.

When the piston moves from the first longitudinal position to the second longitudinal position in the elongated conical chamber, the remaining volume (V _x ) is defined as the volume of the chamber at the position (L _x ), L _x is the length measured from the overpressure side of the piston, for example, to the farthest second longitudinal position (zero point) and the overpressure (P _x ) is the standard pressure, For atmospheric pressure.

V _x = 3.14. [0.00046.S _x ³ + (1.118-0.00139.L) S _x ² + (900-2.236.L + 0.00139.L ² ) .S _x ]

Where V _x is the remaining volume at P _x = z bar that exceeds the standard pressure, V _x = V ₀ / (z + 1)

V ₀ is the total volume of said conical chamber, S = L = total length of said conical chamber,

S _x is one step in the iterative calculation process.

The longitudinal position at which P _x = z bar occurs within a given predefined pressure window (e.g., an overpressure of 1-10 bar) can be iteratively computed by step S (computer software (E.g., 1/1000) of the total length L of the conical chambers measured along the central axis to overcome calculations of unavailable cubic equations. S _x is determined from the above equation, and the x-coordinate of the dot is given as S _x L.

When the chamber includes noncircular portions (e.g., as can be seen in FIGS. 21A and 21B), only the protruding length of the conical wall portions on the central axis is required for the calculation of L and L _x .

The y-coordinate of the dot is confirmed as follows.

When a predetermined maximum force (F _max) is selected, and from a selected zero point on the predetermined central axis of the position of the dots in a predetermined longitudinal position (L _x) can be derived as follows:

D _x = √ F _max /0.008 P _x (P _x (bar), D (mm), F (kgf))

If a laterally symmetrical chamber design is selected as in this figure, the y-coordinate of the dot from the central axis at the longitudinal position (S _x .L) is D _x / 2.

The shape of the chamber wall is the line through all the identified points. In fact, the line can be 'peditized' if it is drawn as a polyline, resulting in a continuous shape of the chamber walls.

19622 deformable fluid

The fluid used inside the actuator piston may be as follows:

1. Vapor media such as air or N ₂ : preferably for CT pressure management systems

2. Combination of gas and liquid

3. Liquids that may be hydraulic oil or H ₂ O: preferably for ESVT pressure management systems

If a liquid is used, it may be more economical to pressurize the actuator piston by moving a predetermined volume of liquid from the actuator piston to and from the actuator piston by the pump, and only a small amount of heat and chill may occur It may not occur at all.

In addition, a reduction in the pressure of the gaseous medium accompanying the heat can lead to freezing of the wall of the actuator piston. This also affects the lubrication of the walls of the chamber and the actuator piston, and thus may affect the efficiency.

Since the liquid can not be compressed, a pressure increase may occur at the end of a significant portion of the piston orbits of the pump. This action is well accomplished, for example, by a crankshaft or camshaft that rotates rapidly, as shown in Figure 901.

Thus, when using Enclosed Space Volume Technology, a liquid as a deformable fluid may be desirable.

19630 Circular chamber  design

The circular chamber shown in Figures 13c and 14d, in which the chamber is movable and the piston (s) may not move, has been divided, for example, into four identical sub-chambers. These chambers have each been configured to be effective in such a way that the forces applied along the circular path on the chamber walls of the respective pistons, which are in different positions within the respective circular sub-chambers, may be the same. This configuration to avoid unnecessary friction causes a reduction in efficiency while adding wear to the piston. The chamber may be subjected to a constant force along the circular path and thus to a constant torque. The size can only depend on the pressure.

Thus, in order to include one or more pistons, it is not necessary to divide the circular chamber into one or more chambers. However, the angle of the wall of the sub-chambers is larger than the angle of the wall of one chamber of the same circle shape as the central axis. Thus, the force of each chamber is greater than when only one chamber is used for multiple pistons.

The chamber shown in Fig. 12B, in which the piston can move and the chamber may not move, may in fact have the same basic design as described above with respect to Figs. 13C and 14D. The piston may apply a force along a constant circular path to the chamber wall.

The subchambers have been configured so that the chamber includes two circular sections of circular cross-section. Each circular section has a single center point and is located in quadrants that face the same distance around the midpoint of the circular center axis of the (sub) chamber. The circular sections are arranged around the central axis of the chamber, which may be circular.

SM-PVT1

In the final version, the (imaginary) common boundary lines 9, 11, 13, 15, 17, 19, 21, 23, 25, 27 are parallel to each other and the central axis 3 of the elongate chamber 1, 21A and 21B in which the common boundary line of the longitudinal cross section of the circular chamber extends from the outermost boundary of the chamber of the cross section to the center axis of the circular chamber, (E.g., the two arrow lines in Figure 27C with two center points). However, in view of the requirement that the maximum force of the actuator within the chamber applied on the chamber wall be independent of the position of the actuator within the chamber and thus independent of the internal pressure of the actuator, , And whether the center point of the furthest circular chamber line of the cross section is the same as the center point of the nearest circular chamber line of the cross section (Figs. 27A to 27C, two center points are assumed).

SM - PVT2

A chamber (having the above-described characteristics) moves in a mating state and / or in a sealed state above the spherical piston (FIG. 10H: the intended configuration of the chamber is shown) disposed in the chamber. By moving the chamber above the piston, a comparable problem arises, as both front wheels of the vehicle rotate around the corner without being arranged at the same distance relative to the center of rotation (?). In order to allow the vehicle to move about a corner, the wheel needs to have independent axes, and both the angle of the wheels and the speed of the wheels in relation to the direction do not have the same value at the same time. Therefore, the reaction forces exerted from the chamber on the contact area of the piston should not be equally divided over the circumferential length of the contact line, but should be the same as the common boundary lines (of the elongate chamber).

Therefore, in this case, the matching state / sealed connection to the wall of the piston as a circular line, a circular spot (the boundary on the nearest end face to the center of the circular chamber) and the circular section (the farthest section from the center of the circular chamber , And may be between the points and sections of different sizes and possibly different shape (s). In order to generate the motion of the chamber, the connection to the wall of the chamber must only be in a matched state, so that the arrangement as described above may not be a great risk. Due to the various sizes of the circumferential surface, the contact is in a sealed state (closest to the center of the circle about the central axis of the chamber) and in a matching state (from the center of the circle about the central axis of the chamber Most distant state), and can be accomplished between any combination of the sealed state and the mating state contacts. This affects the magnitude of the frictional force between the piston and the chamber wall, and is therefore the direction of the intended configuration in which the relative motion can occur (in the home configuration, the orientation must be in the direction of the shape of the chamber) 27c).

To reduce friction, a spherical piston may be rotatable about a piston rod and thus be rotatable about a central axis of the piston rod, the central axis of the piston rod being parallel to an axis passing through the center point of the chamber Sectional section of the chamber.

Actuator  The piston and / Chamber  Geometric shape

Constructions of piston and piston chambers are considered: conical tubes with constant area and variable volume, flexible actuators, walls and contact pistons. The chambers consist of Fermi tubes. Clear calculations of volumes and contact areas are attached to the outlined Maple worksheet. Actuator force distribution is indicated. For purposes of illustrating the importance of geometric shapes, the drawings are somewhat exaggerated.

1. Fermi tube configuration

The center base (center of the "bend" of the chamber), centered on the origin (0,0,0) of the fixed (x, y, z) coordinate system with radius R, Is displayed. See blue circles in Figures 32g and 32h. The vector function of the base circle is standard:

(1.1)

Along this base circle, only the rotational angular interval (u ∈ [0, L]) at which the piston contacts the chamber wall is considered.

In each of the orthogonal planes (see Figs. 1 and 2) with the base circle in the case of u ∈ [0, L], a circle is defined that traces the piston chamber which ultimately contacts the complete chamber and chamber walls. These circles have a radius ( p (u) ) that depends on the base circle parameter (u ∈ [0, L]); The individual centers of the circles are all located on the base circle.

A group of circles draws the trajectory of the tube surface of a so-called Fermi tube around the base circle.

The function p (u) assumes that u is linear so that the corresponding Fermi surface can be called a cone (see corresponding figures 32f, 32g and 32h). The cone effect (which ultimately leads to the driving of the piston inside the chamber) can be achieved by the increasing function of the other u. The linear radius function is as follows (this applies to the specific values α and β of the maple attached data and is used for illustration in this report):

2. Piston and chamber

(1.2)

The FermiTub surface, represented by a parameter with a radius function ( p (u) ) that is 'curved' around the base circle, is given as a vector function:

(1.3)

Where e ₁ ( u) and e ₂ ( u) are orthogonal unit vectors that range in the orthogonal plane of the base circle as shown in Figure 1:

(1.4)

Similarly, the FermiTube solids, which are represented by parameters with a radius function p (u) that is 'curved' around the base circle, are:

(1.5)

It should be noted that the surface is obtained from the corresponding solids by simply setting? = 1:

(1.6)

The volume of the Fermi-tube solids (corresponding to the rotation angle interval [0, L]) is determined as follows:

(1.7) volume =

Here, the Jacobi integral function is given by the one-way function of r as follows:

(1.8)

The area of the Fermi tube surface (corresponding to the rotation angle interval [0, L]):

(1.9) Area =

Here, the Jacobian integral function is:

(1.10)

The maple output data includes the calculation of an example of the total area and the total volume, which are calculated from the values of selected constants that define the geometric shape of the particular case being considered and shown. This is a completely general matter and can be numerically evaluated by selection of other geometric descriptor values.

The total area and total volume include values from the end caps being discussed.

3. Piston and chamber

2. End Cap

The end caps are assumed to be spherical. This shape condition is not absolutely necessary. The prerequisite is the round fitting to the tube portion of the chamber at the handle and both ends of the piston, the total surface area and the sealing volume. All of these are most easily obtained by the spherical end caps with respect to the considerations of this model (see Figures 32d and 32e).

In fact, these old assumptions are not realistic at all:

If fully elastic piston material is given, the average curvature is always constant anywhere there is no contact with the wall. That is, in this setting, the spherical radii at both ends will be the same (there is the same tendency). These conditions are not being implemented in this discussion.

By virtue of the physically correct flexible piston material description, the actual shape of the end caps, the enclosed volume, and the pressure inside the piston at each time point can be estimated.

The area of the spherical cap and the volume to be 'enclosed', ie, the volume removed from the solid spherical body when the cap is cut along the plane, can be represented by simple geometric representations. Thus, this hypothesis of spherical caps continues.

The area of the cap with height h and base radius a is as follows (see Figure 3):

(2.1)

The volume of the cap with height h and base radius a is:

(2.2)

For completion, the radius of the virtual spherical body is displayed, from which the individual end caps are obtained for u = 0 and u = L, respectively:

(2.3)

In the geometry of the tube, the values of a and h are determined solely by the radius function ( p (u) ) and the partial function ( p ' (u) ) at u = 0 and u = : The radius of the base circle has no role!

(2.4)

Thus, assuming that the spherical hypothesis solution is maintained, the end cap areas and volumes are determined solely by the individual values p and p '.

4. Piston and chamber

Since the end cap (s) are supported or attached to the shaft, the spherical geometric shape of the piston end (s) is altered by attachment and resulting forces between the shaft and the piston, in view of the strength of the base circle. Given an exact description of the attachment and piston material, the resulting geometric shape of the deformed end caps can be estimated. This is considered below.

3. Movement of piston and attachment of shaft

The geometry and area for precise contact between the piston and the chamber walls are of paramount importance. Through this contact, the driving force applied to the piston is activated. For this model, the wall contact is modeled by a Fermi tube centered on a given base circle: the volume (pressure) and area (force on the wall) are calculated.

The actual sliding force applied along the walls of the chamber is obtained by a geometrically symmetric (axial centered) double projection of the gray total force on the chamber segment shown in Figures 32h through 32M (inclusive) . Therefore, the resulting sliding force is proportional to the longitudinal length of the segment and the internal pressure of the piston (pressure is force per area).

Depending on the friction model (friction between the chamber wall and the piston) and depending on the material properties of the piston (elasticity, etc.), the resulting force drives the segments longitudinally. The resultant motion of the free piston surface tends to be adjusted as a rotation about the center of the base circle since the force in each segment is proportional to the longitudinal length of the segment and is thus proportional to the distance of the segment from the center of the base circle (Primarily a lot depending on the physical descriptors implied above).

When the piston is attached to the shaft along the base circle of the chamber, the described force can also be applied to pull or push the attached circular shaft in a circular movement about the center of the base circle as well.

19640

5A-5H (inclusive) of EP 1 179 140 B1 discloses a piston comprising six support means 43 rotatably secured to a piston rod 45 about an axis 44 Figures 105A-105H of the application are shown. The other ends of the support means are assembled in an impermeable flexible sheet disposed between the flexible O-rings, and the flexible O-rings are hermetically connected to the walls of the combination of the piston and the conical chamber. Ring is pressed against the wall by the support means due to the pull strings and one side of the pull string is assembled to the piston rod and the other side is assembled to the support means in the vicinity of the O- Allowing the means to spread from the piston rod to the wall of the chamber. Also, a helical spring disposed in a circular path on the impermeable sheet is centered on the center axis of the chamber to press the O-ring against the wall of the chamber, and the support means directly supports the O- It does not. This is the main solution as a solution principle.

According to an unfinished aspect of the present configuration, the impervious flexible sheet is installed in a free suspension state, and the piston (Figs. 5G, 5H) can be pushed inward (change in shape) when pressed by the fluid under the seat . According to another yet totally undeveloped aspect, the O-ring is properly assembled to the support means. In addition, the support means is suitably assembled to the means for holding the O-ring in place between the support means and the assembly points of the O-ring.

There are two preferred solutions for preventing the shape change of the impervious flexible sheet. Although other solutions may be possible, they are not shown here.

According to one solution, the impermeable flexible sheet can be assembled to the end of the piston rod, for example by a screw. In another solution, the sheet can be vulcanized only on and around the piston rod. By fastening the sheet to the piston rod in this way, it is possible (but can not prevent) to substantially reduce the shape change of the sheet upon pressurization. In addition, by properly reinforcing the sheet, the shape change of the sheet can be further reduced. Above all, the sheet may have to be formed with a production size having a circumferential length approximately equal to the circumferential length of the chamber wall at the second longitudinal position. In order to seal the seat against the wall of the chamber, when the piston is moved to the second longitudinal position, in the first example, the seat moves from the second longitudinal position to the first longitudinal direction It may need to be unfolded into position. The pulling springs on said support means can provide a pulling force slightly greater than the pulling force of said impermeable sheet so that when the piston is not in the second longitudinal position, . If the seat is bent upward during pressurization, a third force may be generated to pull the O-ring from the wall. In order to substantially prevent the generation of such forces, concentric stiffeners, which may be formed of a flexible material in the longitudinal direction of the stiffener, or helical stiffeners around the central axis of the piston rod, Of reinforcements. Uses of other stiffeners may be possible, but they are not shown here. The use of the stiffener patterns means that the width of the sheet can be 2D in a transverse plane that is orthogonal to the central axis of the chamber and perpendicular to a direction that is only slightly off center axis of the chamber.

Preferably, the reinforcing layer of the sheet is disposed closest to the high pressure side of the sheet, and another layer not comprising stiffeners may be vulcanized in the first layer described above. The production thickness of each layer can be very thick, so that even if the thickness decreases at the first longitudinal position, it can be sufficient to ensure that the piston performs its proper function for a long time.

Also, the O-ring can be produced with a size whose outer circumferential length is about the same as the circumferential length of the chamber at the second longitudinal position. Also, the O-ring should be produced to have a large diameter sufficient to compensate for the reduction in thickness when the piston is moved to the first longitudinal position.

The impermeable sheet can be vulcanized on the outside and inside of the O-ring to achieve proper sealing when the O-rings are sealingly connected to the walls of the chamber.

A spring in the lying-down state can be vulcanized on the O-ring and impermeable sheet between the ends of the support means. Such a vulcanization treatment is held together as a whole.

Once the impermeable flexible sheet is assembled onto the piston rod, the width of the seat can be substantially expanded by the pulling forces of the springs on the support means and by the rotational force of the support means. The pulling force of the impermeable flexible sheet, the pulling force of the O-ring, the pushing force of the spiral spring in the lying state, the pulling force of the supporting means, and the reaction force of the wall against the O- And the O-ring can be pressed onto the walls of the chamber to achieve a sealed connection. The sprung spring in the lying-down state shown in the prior art figures serving mainly to hold the O-ring in place between the ends of the support means may not provide sufficient force to perform the function as described above have. Instead, a resilient metal rod can hold the O-ring well in place. Both ends of the rod can slide between two adjacent support means and the two rods can slide past each other through the support means.

19650

EP 1 179 140 B1 discloses an elastically deformable means in which the strength is reinforced by rigid members which are rotatably fastened to a common member such as a piston rod, It can be constituted by a deformable means. The elastically deformable means may have a trapezoidal cross-section. When moving from a first longitudinal position to a second longitudinal position within the chamber, the wall of the chamber in a second longitudinal position is parallel to the central axis of the chamber, and the trapezoid becomes increasingly rectangular. When the piston moves from the first longitudinal position to the second longitudinal position, the rigid members can rotate at an angle substantially parallel to the central axis.

The foam may expand from a second longitudinal position within the elongate chamber to a larger configuration at a first longitudinal position. However, such expansion is done in a different way than a method of inflating an inflatable container, wherein the circumferential length comprises a flexible wall having a production size approximately equal to the circumferential length of the wall of the chamber at the second longitudinal position (See for example EP 1 384 004 B1). The thickness of the wall of the container can be reduced ("balloon effect") when it is moved to the first longitudinal position and can be matched to the wall of the chamber.

CLAIMS 1. A motor of the type wherein the pump has a piston which is moveable in the interior of the chamber in a mating and / or sealing manner,

- the elastically deformable means are formed of a polyurethane foam,

- PU foams include polyurethane memory foam and polyurethane foam,

- Polyurethane foam is made up of polyurethane memory foam in much of the polyurethane foam.

Elastically deformable means can be formed of foam. Particularly, since the moving piston inside the chamber of the pump, for example, can be formed of polyurethane foam, good characteristics can be exhibited even in a harsh environment.

When moving from the second longitudinal position to the first longitudinal position, the size of the foam can be increased by increasing the size of the cells in which the fluid may be present inside the chamber. This increase in size may be possible if the cells are open, that is, if the interior of the cells can communicate with the atmosphere around the foam of the chamber. Thus, at the second longitudinal position, the foam must be under a predetermined pressure to reduce the size of the open cells of the foam, and at the second longitudinal position, the foam will expand itself when moved to the first longitudinal position To be under pressure. The material of the foams, and thus the walls of the open cells, must have considerable resilience. These materials may be polyurethane (simply ' PU &apos;) foam, and the highly flexible type PU foam may be a so-called memory foam.

A material with substantial flexibility, however, can not withstand significantly high pressures on its own, and the piston must be constructed to withstand high pressures. In order to obtain better pressure resistance, a sandwich structure can be used. For example, two PU layers may be provided, one of which may be formed of a PU memory foam and the other of which may be formed of a PU foam that is less flexible than a PU memory foam. These two layers can be glued together. In the absence of such layers and / or space for sandwich structures, the creation of such layers and sandwich structures may be difficult, and thus a mixture of PU foam and PU memory foam may be a solution. The proportion of normal PU form can occupy a small portion of the total mixture.

In which the pump comprises the piston,

The support members can be bent,

- the support members exhibit a predetermined bending force,

The members being lockable in the interior of a holder connected to the piston rod and rotatable about the bend of the rigid member of the holder,

The end being under the pressure of the adjustable member,

The longer end of the rigid member has an increased thickness.

The memory foam material quickly recovers to its original size at normal operating temperatures, such as &lt; RTI ID = 0.0 &gt; 10 C &lt; / RTI &gt; At lower temperatures, such as about freezing point, a longer time is required, which may be too long to meet the requirements of the mating state and / or the sealed state connection to the walls of the chamber. When the piston moves from the second longitudinal position to the first longitudinal position, the rigid members may be formed of a spring material so that the rigid members can press the foam outward. A predetermined bending force may be required and an end portion of the stiffening member, for example, having a length substantially shorter than the total length of the stiffening member may be bent so that the end of the rigid member, Can be combined. The holder may be connected to the piston rod. A predetermined bending force can be achieved by the adjustable member pressing the short end of the rigid members. The adjustable member may be a rotatable member that can be locked in place.

When moved from the first longitudinal position to the second longitudinal position, the foam may be urged inward by the walls of the chamber and the foam may have a shape in which no lateral force is present, The casting foam which is glued to the members (preferably formed of polyurethane) loosens and can lose its function.

In order to prevent the rigid members from loosening, other measures are taken to increase the thickness of the long end of the rigid members near the position where pressure is obtained from the fluid beneath the piston of the chamber.

In which the pump comprises the piston,

Said impervious flexible layer having a size during production in a non-stressed state is formed in a size having a circumferential length approximately equal to the circumferential length of the chamber wall in the second longitudinal position.

A foam piston with open cells is matingly connected to the wall of the chamber. In order to enable the foam piston to be sealingly connected to the chamber wall, it is necessary to add an impermeable layer such as a natural rubber type. This layer may have to be formed with a circumferential length approximately equal to that of the inflatable container type piston. Thus, the layer may have to be formed to a size having a circumferential length of the chamber wall at a second longitudinal position in a stress-free state, and thus may have to be assembled around the foam under pressure. When moved from the second longitudinal position to the first longitudinal position, the foam and therefore the rigid members need to be pressed in the form of a foam (trapezoidal) with the layer positioned in the first longitudinal position. Upon returning to the second longitudinal position, the layer can be retracted into a generally rectangular shape of the foam in a second longitudinal position: this layer requires flexibility. In order to allow the open cell to be able to communicate ("vent") when moving from the second longitudinal position to the first longitudinal position and vice versa, the impermeable layer is configured such that the ratio of the piston communicates with the fluid on the pressure side Should be able to.

19650-1 For example, Pumping  Improved Suspension Structure of Foam Pistons for Use

WO 2000/070227 discloses a foam piston having the problem that the foam can not be properly mounted on the piston rod, especially during a return stroke. This is because the PU foam can not be fastened to the steel of the piston rod. In addition, it is difficult to immediately release the piston from the mold due to the fact that the angles of the rows of reinforcing pins increase from the piston rod side toward the outside. As yet another difficulty, since the surface is roughly formed as described above, the PU foam is not well fastened on the metal reinforcing fin. An improved foam piston suspension structure is the subject of this section of the patent application.

The piston disclosed in the 19650 section of the present patent application has considerable robustness for professional use. For example, when used in a bicycle pump, it may require a configuration that is less robust but reliable and simple to repair and uncomplicated.

Such a solution is subject to the features of the independent claim.

For example, if the metal fins contain a surface coating of a suitable material, for example PU, if the piston foam is also formed of PU, the metal pins will continue to be used until the foam piston is molded around the fins . Fins are sufficiently fastened to the foam to prevent the foam from peeling away from the piston. The metal pins may be formed of a material of the magnetizable steel type. When the holder plate on which the fins are designed to transmit a compression force from the high-pressure side of the piston to the piston rod is magnetized, the fins can be adhered to the inside of the small holes of the surface with approximate depth of the diameter of the fins . The holes may have a geometric design that allows the pins to rotate within the holes. The pins and the holder plate are fastened to each other as soon as they are positioned sufficiently close to each other so as to be influenced by the magnetic force. The holder plate can be small in thickness and can be glue-bonded to the piston rod and can be glue-bonded directly or indirectly to a holder assembled to the piston rod.

According to yet another improved version, the pins are formed in such a way that, for example, the PU plasticizer, which is fully attached to the foam of the same type (e. G., PU foam) . There is a further possibility to prevent the PU foam from being stripped from the pins by significantly reducing the diameters of the fins. The suspension mount of the pins can be made as follows. The pins can have a spherical body end that can be pressed smoothly in a holder plate having a spherical cavity so that the spherical body end can rotate in the spherical cavity. The fins can have a predetermined preload, which increases the width of the foam when the piston moves from a second longitudinal position to a first longitudinal position of the chamber, especially at lower temperatures. This increase in width can be achieved in such a way as to provide a small lever arm at the spherical end of the pins, which is attached to a plate of flexible material, for example rubber. The angle of production is larger than the widest angle of the piston when the piston is in the first longitudinal position of the chamber.

19660

EP 1 179 140 B1 discloses an inflatable container piston type, whereas according to EP 1 384 004 B1, this type of piston has a first longitudinal position to a second longitudinal position In order to prevent the piston from being pinched during movement, the production size of the non-stressed state should be such that the circumferential length in the second longitudinal position of the elongate chamber is approximately equal to the circumferential length of the chamber.

The piston expands when it is moved from the second longitudinal position to the first longitudinal position. According to EP 1 384 004 B1, the stiffener for this desired behavior can be a layer in which the reinforcing strings are arranged parallel to one another in a production model with no stress, such strings having two end parts connected to each other One of these end pieces being mounted on the piston rod and the other being able to slide on the piston rod. Rubber is directly vulcanized on both ends. Such a reinforcing layer is an inner layer, and another layer thicker than the layer with reinforcing strings is used to protect the reinforcing layer. Both layers may be vulcanized together, and at the end portions, another extra layer may be provided on top of these two layers. The function of the second layer is also to prevent the reinforcing strings from &quot; protruding &quot; from the outside of the outer layer, so that the mating adhesion with the walls of the chamber is good but the sealing contact with the wall of the chamber is not possible. (Second longitudinal position) in the chamber of the pump (see 19620) where a constant force is applied to the piston rod, for example, when the second layer is disposed on top of the reinforcing layer, To about 59 mm (first longitudinal position). If the two reinforcing layers are arranged above and below each other at a significantly small overlapping angle and are disposed on the above-mentioned 'second' layer, the strength of the container is further increased, but even a 330% expansion is possible.

Different types of rubber may be used for the rubber layer, but they must be compatible so that they can be vulcanized together without loosening under normal operating conditions.

It has been observed that even if the ellipsoidal container type piston is fully expanded into a spherical body shape, the probability of failure is considerably high. For this reason, the design can be modified to increase the length of the piston as a stress-free production model by maintaining other variables such as the non-changing chamber design. Therefore, it may not reach the shape of a spherical sphere, and an ellipsoid having a shape close to that of a substantially spherical sphere may not expand to 330%. This ensures the reliability of the piston even when there is only one layer with the stiffener.

The container in the no stress production state can be formed in a shape in which the wall of the container is not parallel to the central axis but parallel to the walls of the chamber because the wall of the chamber at the second longitudinal position is not parallel to the central axis have. In the stressless production state, only the walls of the chamber are independent of the walls of the container.

19660-1.2 Actuator  Piston function update

The actuator piston includes a container including a wall around the cavity, the cavity being inflatable and pressurizable by the fluid and / or may comprise a foam, The chamber is moved from a second longitudinal position to a first longitudinal position, the chamber comprising sections having different cross-sectional areas, wherein the first and second longitudinal positions are different in circumferential lengths and the first and second longitudinal positions Sectional areas and circumferential lengths at the intermediate longitudinal positions between the first and second longitudinal positions are at least substantially continuously different and the wall of the container of the actuator piston slides on the wall of the chamber, The cross-sectional area and the circumferential length are smaller than the cross-sectional area and the circumferential length at the first longitudinal position.

In this case, the chamber also has cross-sectional areas with different cross-sectional areas and the same circumferential lengths at the first and second longitudinal positions and intermediate longitudinal positions.

The wall of the piston may preferably be symmetrical in the longitudinal direction of the chamber between the end caps (movable end and non-movable end) about a transverse center axis. Each symmetrical half includes longitudinal cross-sections having different cross-sectional areas, different circumferential lengths, at least substantially continuously different cross-sectional areas, and circumferential lengths in the intermediate longitudinal positions between the transverse central axis and the end cap do.

In this case, the circumferential lengths may be the same.

By providing a reinforcing layer on the wall of the container of the actuator piston, when pressed inside the cavity of the container, the outside of the wall is formed in a smooth shape, preferably in a convex shape. As a result, the contact area of the wall of the chamber becomes small. The inflating force of the wall of the container is applied in a direction perpendicular to the surface of the wall of the chamber. The inflation force may be considerably larger than the internal pressure of the cavity of the actuator piston, in particular in the case of t / R <<<, depending on the t / R ratio (R = lateral radius of the longitudinal section, t = wall thickness of the actuator piston) .

If the actuator piston is disposed in a wall of the chamber having a positive angle with the central axis of the chamber in the direction from the second longitudinal position to the first longitudinal position, asymmetry is caused in the reaction force from the wall of the chamber . This is because no reaction force is generated on the chamber positions closest to the first longitudinal position of the chamber on the last position closest to the first longitudinal position portion of the contact area (wall chamber-container) The walls of the container are bent toward the walls of the chamber at these positions until the reaction force becomes equal to the expansion force of the wall of the container. The walls of said container of actuator pistons roll over the walls of said chamber. This rolling motion is added to the contact height of the contact area of the wall of the chamber and the wall of the container, thereby increasing the frictional force. Such expansion of the wall of the container of the actuator piston causes a slight pressure drop inside the wall of the container and when the volume of the enclosed space is kept constant the expansion force of the wall of the piston is reduced by the pressure drop , The frictional force also decreases. Movement (sliding) of the actuator piston to the first longitudinal position may occur. This reduces the contact height because the circumferential length of the wall portion of the container closest to the second longitudinal position and thus the circumferential length of the contact region closest to the second longitudinal position can also be reduced .

Due to the lubrication between the wall of the chamber and the wall of the container, the propulsive force is still greater than the frictional force and the actuator piston slides to a new chamber position close to the first longitudinal position until the asymmetry of the force occurs again And the cycle can then be resumed.

By increasing the contact height at the longitudinal cross section of the wall of the chamber and the matching wall of the container (rolling motion), the height immediately following the existing height can be made larger. The main cause of this height increase is the behavior of the actuator piston.

For example, in the case of an elliptical actuator piston, there is a means by which it can operate as described above:

If such means are present, the reinforcing direction of the bendable reinforcing layer of this means is the longitudinal direction substantially parallel to the central axis of the chamber,

There is almost no reinforcing layer in the transverse direction,

Preferably, the walls of the container are symmetrical about the transverse symmetry axis,

The wall surface of the actuator piston is smooth at least continuously on the contact area with the wall of the chamber and directly adjacent the contact area.

The wall of the container is bent outwardly from the final circumferential surface of the contact region closest to the first longitudinal position between the wall of the chamber and the wall of the container under internal pressure to reach the wall of the chamber,

Further, the wall of the container in the vicinity of the second longitudinal position is withdrawn from the wall of the chamber under the bending action, and then the contact surface area between the wall of the container and the wall of the chamber is reduced again.

If the internal pressure for pushing the wall of the container of the actuator piston toward the wall of the chamber may not be sufficient, the actuator piston is stopped from operating toward the first longitudinal position, causing a circumferential leakage. For example, in the case of the chamber shown in the 19620 section of the present patent application, this phenomenon can occur if there is an overpressure of 1 bar at the common interface inside the chamber-this is referred to as the '"

In fact, when the pressure inside the cavity of the actuator piston is significantly low, there is a behavior in which the movable cap of the container of the actuator piston located closest to the first longitudinal position moves stepwise.

This is because, in addition to the expansion of the wall of the container due to the internal pressure, the expansion of the walls of the actuator piston, when moved from the second longitudinal position to the first longitudinal position, Additional force may be applied to the contact area of the wall of the near chamber and the wall of the actuator piston, resulting in increased frictional forces.

When the non-removable cap is located closest to the first longitudinal position and therefore in the direction of movement in the &quot; head &quot; of the container, the pressure is even lower and smooth movement is possible. The reason may be that the extra inflation force of the wall of the container can be added to the reduced inflation force that does not exceed the frictional force.

Thus, when the wall of the piston is formed of a flexible reinforcement material and is pressurized by a pressure source passing through the enclosure space, a smooth outer surface of the piston wall results, Providing a contact height in a circumferential direction in the longitudinal cross-section of the piston, the height of which varies in size during movement of the piston in the intermediate longitudinal positions between the first and second longitudinal positions.

This sliding movement can take place over several different contact areas of the wall of the chamber and the wall of the actuator piston. This is possible because the wall of the container is convex in shape and flexible while a plurality of different contact areas are arranged in succession to each other.

19660-2 Expansion Piston - Strength and Stiffness

An expandable piston of the type in which the ellipsoid becomes an expanded ellipsoid / (almost) spherical body at the second longitudinal position of the chamber can be compared to a cylindrical bezel with a small wall thickness under internal pressure, in terms of strength and stiffness.

Hoop stress (σ _H ) causes the wall of the cylinder to expand. The size of the hoop stress? _H ¹ is generally about 10x the magnitude of the internal pressure of the cylinder ² . This is because, according to the present patent application 19620 section, an actuator piston with a low internal pressure is fired from the second longitudinal position of the cylinder to the first longitudinal position.

(1: σ _H = pR / t, p is the internal pressure, R is the 1/2 diameter of the cylinder, t is the wall thickness of the cylinder,

2: Strength and Stiffness of Engineering Systems published by Springer, Dabello, Frederick A Leckie, and Dominique J in 2009.

The magnitude of the hoop stress? _H depends on the longitudinal position of the piston, the size of the chamber and the number of reinforcing layers - in the case of one reinforcing layer,

The second longitudinal position / diameter 17 mm is approximately 3x the internal pressure of the piston,

The first longitudinal position / diameter 58 mm is approximately 3.8x the internal pressure of the piston.

An expanding piston of the type in which the spherical body becomes the enlarged spherical body at the second longitudinal position of the chamber can be compared with the spherical spherical vessel having the small wall thickness under the internal pressure with respect to the strength and the stiffness.

The applied spherical body stress (σ _S ) ³ can be compared with the longitudinal stress (σ _L ) of the cylindrical cylinder which is half the size of the hoop stress (σ _H ). This means that the spherical piston inside the circular chamber can provide a thrust of half the thrust of the ellipsoid. Thus, in order to reduce the size of the motor while achieving a comparable torque, more than one spherical piston may be available in the circular chamber.

(3: sigma _S = pR / 2t, p is the internal pressure, R is the 1/2 diameter of the cylinder, and t is the wall thickness of the sphere)

Therefore, stress which expands the wall of the actuator piston in relation to the transverse radius (R) of the actuator piston depends on the thickness (t) of the wall of the actuator piston and the actuator piston pressure _{C x = [1-t /} R ] Times. As R can depend on the transverse radius of the chamber, C _x can be different between the longitudinal position of the actuator piston and the other longitudinal position. Energy can thus be saved and the amount of energy savings depends on the slope of the wall of the chamber since the propulsive force of the actuator piston is the sine of the angle between the expansion force x the longitudinal center axis of the actuator wall and the wall of the chamber. The greater the angle, the greater the propulsive force.

As an example, as an alternative to a petrol motor for the Golf MK II, the cylinder diameter is 81 mm, the stroke length is 77.4 mm and the size of the motor operating at 9-10 bar is known.

The slope of the chamber is selected as α = 10 ° and thus sine 10 ° = 0.174, while the diameter of the cylinder at the first longitudinal position is maintained at 81 mm, so that the diameter at the second longitudinal position is 53.7 mm , The wall thickness of the actuator piston is 3.5 mm, the pressure at the second longitudinal position is 10 bar and the pressure at the first longitudinal position is 2.25 bar.

C ₁ = R / t [1-t / R] = 10.6?? _H2 = 24 N / mm &lt; ² &gt; → F _{Propulsion 1} = 2125N

C ₂ = R / t [1-t / R] = 6.7?? _H1 = 67 N / mm &lt; ² &gt; → F _{Propulsion 2} = 3933N

Conclusion: A motor according to the present invention having approximately the same size as the present gasoline motor can be used.

19680-2 Pump piston containing container

The purpose of this section is to enable the use of the piston of the piston, in which the circumferential length in production of the piston is equal to the circumferential length in the second longitudinal position, using the principle disclosed in WO 2002/077457 Container type piston. This means that the inflatable container type piston is inflated to move from the second longitudinal position to the first longitudinal position without incision, and then returned. However, as can be seen empirically, the traveling consisting of rolling-sliding-rolling motion from the second longitudinal position to the first longitudinal position is only due to the internal pressure of the piston, A continuous outer wall, an area of contact with the wall of the chamber disposed below the transverse centerline of the piston, and a moveable cap closest to the first longitudinal position, the non-movable cap having a second longitudinal position It is located closest to you.

As will be appreciated, self-propulsion is an extraneous capability when the wall of the chamber is parallel to the central axis of the chamber. Thus, in order to use the piston in the pump, self-propelled movement, i. E. "Rolling motion" of the wall of the piston above the wall of the chamber must be prevented. This can be achieved by the discontinuity of the outer wall of the piston.

The generation of a self-propelled actuator piston, "rolling, sliding or rolling motion of the wall of the piston on the wall of the conical chamber ", should be avoided, since it generates thrust in the opposite direction of the pumping force. To this end, the contact area between the wall of the chamber and the wall of the piston may have to be limited ("discontinuous") to a predetermined area of the wall of the piston, which can be done in at least two ways:

The contact area can be a separate part of the wall of the piston - the contact area can be extended in the rest of the wall of the piston.

The portion of the piston closest to the second longitudinal position may have a cross-sectional circumferential length less than the cross-sectional circumferential length of the contact region.

Foam stresses in the wall of an inflatable container type piston (see sections 19660, 207 and 653 of the present patent application) cause an expansion of the circumferential length of the wall and are the source of the actuator piston to self-propel by internal overpressure .

Thus, the hoop stress has a great influence on the sealing ability of the piston with respect to the chamber wall, and consequently, the hoop stress simultaneously, when the piston is pushed from the first longitudinal position to the second longitudinal position, (jam) capability. Due to the specific R / t ratio (large radius compared to the small thickness of the walls (layer with the reinforcing layer (s))), the hoop stress is considerably higher than the internal pressure. What is initially believed is that the pressure of the gaseous medium inside the piston can be "lower" in relation to the pressure of the medium compressed by the piston inside the chamber in which the piston is located. However, the piston must be sealed at the pressure of the medium to be pumped.

At the same time, it seems impossible to manually push an inflatable (compressible medium such as N ₂ ) piston (as shown in the section) in the chamber shown in the 19597 section of the present patent application. Wherein the piston comprises a compressible medium having an overpressure (atmospheric pressure or more) of 1 1 1/2 bar (absolute) at a first longitudinal position, and wherein the piston extends from the first longitudinal position to a second longitudinal position, The medium may preferably be as follows:

It may be even more desirable if, for example, a foam, which is different from a compressible medium such as a gas, can contain a fluid inside the hole, and if the foam has an open structure , The foam should preferably be at atmospheric pressure, optionally at a low overpressure (e.g., 1 bar), in the first longitudinal position. Preferably, the foam, not the medium, should extend the wall of the piston, optionally it may be a combination of the two factors,

And / or different from a compressible medium such as an incompressible medium (e.g., a liquid such as water)

● When the foam is compressed by the wall of the piston, in order to prevent the sudden rise of the internal pressure and thus the possible interposition of the piston rod, in communication with the enclosed space, for example a hollow piston rod, Moving from this first longitudinal position to the second longitudinal position causes the foam to escape from the container to the enclosure space (e.g., WO 2010/094317 or sections 207 and / or 653) .

According to an alternative solution for preventing the creation of a self-propelled actuator piston when an inflatable piston is used, the piston can comprise a wall with or without a reinforcing component, so that the reinforcement can be minimized , Which prevents excessive swelling of the wall of the piston and of the foam, preferably the open cell foam, upon expansion. The open cells may comprise a fluid, preferably a gaseous medium, alternatively a liquid or a combination of a liquid and a gaseous medium. The foam can be inserted into the piston when the piston is in the first longitudinal position and the wall of the piston is connected in a mating and / or sealing manner to the wall of the chamber, 2 &lt; / RTI &gt; position), the foam will fill the piston most optimally when the wall thickness is less than the tension. The foam may be compressible at a high level (e.g., 5: 1 using a piston of 19660 and / or 19680 sections) so that when the piston is in a second longitudinal position where all open cells are closed, It can be charged with a higher foam. When moving from the first longitudinal position to the second longitudinal position, the medium inside the foam can be removed from the piston, for example, with a piston rod. To prevent high pressure build up inside the piston rod, the piston rod may be a moveable piston that reduces the volume of the medium of the open cell (if not in the second longitudinal position). By this high pressure, when moving from the first longitudinal position to the second longitudinal position, the piston becomes an actuator piston, which causes a pinch phenomenon. As a result, the size of the piston can be changed (and the shape of the piston can also be changed) during the pump stroke, without self-moving, and without a pinch phenomenon, by a sufficient sealing force against the wall of the chamber. As the wall of the piston is formed of a flexible material, for example rubber, the piston functions as a reliable piston for the pump.

The production of the container piston comprising the foam is as follows: the wall of the container piston is produced when in the second longitudinal position. Thereafter, fluid is injected into the cavity of the container when in the first longitudinal position. The movable cap is moved toward the other cap, and the wall of the container is bent. The position of the movable cap is then fixed, and then the fluid is deflected from the cavity. The foam mixture is injected, and the cavity of the container is closed. After the curing process, the fixation of the movable cap is removed. Contraction of the wall of the container may occur due to the nature of the foam comprising the open cell. This contraction can be compensated in such a way that the pressure of the medium inside the open cell is increased only slightly, or in the manner of providing another cavity inside the impervious flexible wall disposed inside the center of the foam, And the wall urges the foam towards the wall of the container piston to allow the wall of the container piston to reach its originally planned position.

A separate wall portion of the piston 'protrudes' from the wall of the piston. Thus, the circumferential length of the remaining portion of the adjacent wall is larger, while the circumferential length of the circumferential transition portion from the wall of the piston to the other portion changes substantially or steplessly in the circumferential direction.

The contact area of the wall of the chamber and the discrete portion may be small. This can be done by selecting a distinct part, for example the exact shape of the circular segment. The top of the segment contacts the walls of the chamber.

207

In general, for example, the new design of a combination of a chamber and a piston for a pump is such that the force applied to actuate the pump during the entire pumping operation is low enough to make the user feel comfortable, It is suitable for women and adolescents, does not prolong the pumping time, and ensures that the pump is made of a minimum of reliable components and requires little maintenance time.

In a first aspect, the present invention relates to a combination of a piston and a chamber,

The chamber defines a elongate chamber having a longitudinal axis,

The chamber has a first cross-sectional area at a first longitudinal position of the chamber and a second cross-sectional area at a second longitudinal position, the second cross-sectional area is at most 95% of the first cross-sectional area, At least substantially continuously between longitudinal positions, and the piston is configured to conform to a cross-section of the chamber when moving from a first longitudinal position to a second longitudinal position of the chamber.

In the present context, the cross section is preferably perpendicular to the longitudinal axis.

Also due to this fact, the cross-section of the chamber preferably changes at least substantially continuously in order to allow the piston to be sealed against the inner wall of the chamber during movement between the first and second longitudinal positions, In other words, there is no abrupt change in the longitudinal cross section of the inner wall.

In the present context, the cross-sectional area of the chamber is the cross-sectional area of the interior space at the selected cross-section.

Thus, as will become apparent from the following description, the area of the inner chamber is varied, resulting in the possibility of actually being fitted to a combination of many situations.

In a preferred embodiment, the combination is used as a pump, the air is compressed by the movement of the piston, and the compressed air is discharged through the valve, for example, to the tire. The area of the piston and the pressure on the other side of the valve determine the force required to provide the flow of air through the valve. Thus, adjustment of the required force can be made. Also, the volume of air provided depends on the area of the piston. However, the first translational motion of the piston to compress the air is relatively easy (the pressure is relatively low), so that such translation can be performed over a large area. Thus, overall, a greater amount of air can be provided at a given pressure during a single stroke of a given length.

Naturally, the actual area reduction depends on the power of the problem as well as the intended use of the combination.

Preferably, the second cross-sectional area is 95 to 15% of the first cross-sectional area, for example, 95 to 70%. In some situations, the second cross-sectional area is approximately 50% of the first cross-sectional area.

A number of different techniques may be used to realize such a combination. These techniques are further described in connection with the following aspects of the present invention.

According to one of these techniques,

A plurality of at least substantially rigid support members rotatably coupled to the common member,

- elastically deformable means supported by the support members to be sealed against the inner wall of the chamber,

The support member is rotatable between 10 [deg.] And 40 [deg.] Relative to the longitudinal axis.

In this case, the common member can be attached to the handle for use by the operator, and the support members extend in the opposite direction from the handle, inside the chamber.

Preferably, the support members are rotatable at least approximately parallel to the longitudinal axis.

Further, the combination may further comprise means for deflecting the support members against the inner wall of the chamber.

According to another technique, the piston comprises an elastically deformable container comprising a deformable material.

In this case, the deformable material may be a fluid or fluid mixture, such as water, steam, and / or gas, or a foam.

Also, in the longitudinal cross-section, the container may have a first shape in the first longitudinal direction and a second shape in the second longitudinal direction, the first shape being different from the second shape.

Also, at least a portion of the deformable material may be compressible, and the area of the first shape is greater than the area of the second shape.

Alternatively, the deformable material may be at least substantially incompressible.

The piston may include an enclosed space in communication with the deformable container, the enclosed space having a variable volume. Such a volume may be varied by the operator and may include a spring biased piston.

According to another technique, the first cross-sectional shape is different from the second cross-sectional shape, and the change in cross-sectional shape of the chamber is at least substantially continuous between the first and second longitudinal positions.

In this case, the first cross-sectional area is at least 5%, preferably at least 10%, such as at least 20%, preferably at least 30%, such as at least 40%, preferably at least 50% %, Such as at least 60%, preferably at least 70%, such as at least 80%, preferably at least 90%.

The first cross-sectional shape may be at least substantially circular, and the second cross-sectional shape may have a first dimension, such as an elongated shape, such as an oval, wherein the first dimension is at least twice the dimension that is at an angle to the first dimension, For example at least 3 times, preferably at least 4 times.

Also, the first cross-sectional shape may be at least substantially circular, and the second cross-sectional shape includes at least two substantially substantially elongated portions, such as a lobe shape.

Further, in the cross-section at the first longitudinal position, the first circumferential length of the chamber is preferably 80 to 120%, for example 85 to 115%, of the second circumferential length of the chamber in the second longitudinal cross- For example, 95 to 105%, preferably 98 to 102%. Preferably, the first circumferential length and the second circumferential length are at least substantially equal.

According to an optional or further description,

An elastically deformable material whose cross section is adjusted in accordance with the cross-section of the chamber when moved from the first longitudinal position to the second longitudinal position of the chamber, and

Shaped flat spring having a central axis along at least substantially the longitudinal axis and disposed adjacent to the elastically deformable material to support the material elastically deformable in the longitudinal direction.

In this case, the piston may further comprise a plurality of flat support means arranged between the elastically deformable material and the spring, the support means being rotatable along the interface between the spring and the resiliently deformable material .

The support means can be configured to rotate from the first position to the second position, wherein in the first position, the outer boundary can be included inside the first cross-sectional area, and in the second position, .

In a second aspect, the present invention relates to a combination of a piston and a chamber,

The chamber defines a elongate chamber having a longitudinal axis,

The chamber has a first cross-sectional area at a first longitudinal position and a second cross-sectional area at a second longitudinal position, wherein the first cross-sectional area is greater than the second cross-sectional area, and the cross-sectional area of the chamber is between the first and second longitudinal positions At least substantially continuously,

Wherein the piston is configured to adjust the cross section in accordance with the cross section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber,

A plurality of at least substantially rigid support members rotatably coupled to the common member,

- elastically deformable means supported by the support members to be sealed against the inner wall of the chamber,

The support members are rotatable between 10 [deg.] And 40 [deg.] Relative to the longitudinal axis.

Preferably, the support members are rotatable at least approximately parallel to the longitudinal axis.

Thus, the piston can be adjusted to different areas and / or shapes, and in this configuration, the piston includes a plurality of rotatably fastened means for holding the sealing means. According to one preferred embodiment, the piston is generally umbrella-shaped.

Preferably, the common member is attached to a handle for use by an operator, for example, when the combination is used as a pump, and the support members extend in a relatively opposite direction from the handle, inside the chamber. This has the advantage of increasing the sealing force by simply applying a force to the sealing means and the support means against the walls of the chamber by increasing the pressure in such a way that the handle is forced into the interior of the chamber.

Also, to ensure that sealing after one stroke is achieved, the combination preferably includes means for deflecting the support members against the inner wall of the chamber.

In a third aspect, the present invention relates to a combination of a piston and a chamber,

The chamber defines a elongate chamber having a longitudinal axis.

The chamber having a first cross-sectional area at a first longitudinal position and a second cross-sectional area at a second longitudinal position, wherein the first cross-sectional area is greater than the second cross-sectional area, and the cross-sectional area of the chamber is between a first longitudinal position and a second longitudinal direction At least substantially continuously between the positions,

Wherein the piston is configured to adjust the cross section in accordance with the cross-section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber,

The piston includes an elastically deformable container including a deformable material.

Thus, by providing an elastically deformable container, the area and / or shape can vary. Naturally, such a container must be sufficiently fastened to the piston so as to follow the rest of the piston when the piston is moved out of the chamber.

The deformable material may be a fluid or a mixture of fluids, such as water, steam, and / or gas, or a foam. Such materials, or some of these materials, such as gas or a mixture of water and gas, can be compressible, or at least substantially incompressible.

If the cross-sectional area changes, the volume of the container may change. Thus, in the longitudinally piercing cross-section, the container may have a first shape in the first longitudinal direction and a second shape in the second longitudinal direction, the first shape and the second shape being different. , At least a portion of the deformable material is compressible and the area of the first shape is greater than the area of the second shape. In this case, as the total volume of the container changes, the fluid must be compressible. Alternatively or alternatively, the piston may include a second enclosure space in communication with the deformable container, and the enclosure space has a variable volume. In this way, if the volume of the deformable container changes, the enclosed space can be filled with fluid. The volume of the second container can be changed by the operator. In this way, the total pressure or the maximum / minimum pressure of the container can be changed. Also, the second enclosed space may include a spring biased piston.

It may be desirable to provide a means for defining the volume of the enclosure space so that the fluid pressure in the enclosure space is related to the fluid pressure between the second longitudinal position of the container and the piston. In this way, the pressure of the deformable container can be varied to achieve proper sealing.

A simple method is to provide means configured to form a pressure at least substantially equal to the pressure between the second longitudinal position of the container and the piston inside the containment space. In this case, a simple piston may be provided between the two pressures (to prevent leakage of fluid in the deformable container).

In fact, the use of such a piston can define the relationship between the pressures, in which the enclosed space in which the piston is translated can be tapered in the same manner as the main chamber of the combination.

To overcome friction and shape / dimensional changes to the chamber walls, the container may comprise an elastically deformable material including stiffener means such as fiber reinforcement.

During the translational movement of the piston from the first longitudinal position to the second longitudinal position, or vice versa, to achieve and maintain a proper seal between the container and the chamber wall, It is desirable that the same internal pressure be higher than the highest pressure of the ambient atmospheric pressure.

In yet another aspect, the present invention relates to a combination of a piston and a chamber,

The chamber defines a elongate chamber having a longitudinal axis,

The chamber having a first cross-sectional area and shape at a first longitudinal position and a second cross-sectional area and shape at a second longitudinal position, the first cross-sectional shape being different from the second cross-sectional shape, At least substantially continuously between the longitudinal position and the second longitudinal position.

The piston is adapted to be adjusted in cross section in accordance with the cross section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber.

This is a fairly interesting one, for example, based on the fact that different shapes of geometric shapes change the relationship between circumferential length and area. In addition, changes between the two shapes are made in a continuous manner so that the chamber has one cross-sectional shape at one location and a different cross-sectional shape at the second location, while maintaining desirable smooth variations of the chamber interior surface .

In this context, the shape of the cross section is the overall shape despite its size. Two circles have the same shape, even if they differ from one diameter to the other.

Preferably, the first cross-sectional area is at least 5%, preferably at least 10%, such as at least 20%, preferably at least 30%, such as at least 40%, preferably at least 10% For example at least 60%, preferably at least 70%, such as at least 80%, for example at least 90%.

In a preferred embodiment, the first cross-sectional shape is at least substantially circular, the second cross-sectional shape has a first dimension in the elongated shape such as an ellipsoid, and the first dimension is a dimension of the cross- At least 2 times, for example at least 3 times, preferably at least 4 times.

In another preferred embodiment, the first cross-sectional shape is at least substantially circular, and the second cross-sectional shape comprises at least two substantially at least substantially elongated portions, such as a lobe shape.

In the first longitudinal position of the cross section, the first circumferential length of the chamber is between 80 and 120%, for example between 85 and 115%, preferably between 90 and 120%, of the second circumferential length of the chamber in the second longitudinal direction of the cross- 110%, for example 95 to 105%, preferably 98 to 102%. Problems can arise when attempting to seal the wall where the dimensions change due to the fact that the sealing material must provide sufficient sealing and dimensional changes. In the case of the preferred embodiment, when the circumferential length variation is low, the sealing can be controlled more easily. Preferably, the first circumferential length and the second circumferential length are at least substantially the same so that the sealing material merely warps but does not extend to a significant degree.

As an alternative, it may be desirable for the circumferential length to slightly change during bending or deformation of the sealing material such that, for example, one side of the sealing material is compressed and another side is elongated by the bending phenomenon. Overall, it is desirable to provide the desired shape with a circumferential length that is at least close to the shape in which the sealing material is automatically "selected &quot;.

One type of piston, which can be used in this type of combination,

A plurality of at least substantially rigid support members rotatably coupled to the common member,

- elastically deformable means supported by the support members to be sealed against the inner wall of the chamber.

Other types of pistons include an elastically deformable container comprising a deformable material.

Another aspect of the invention relates to a combination of a piston and a chamber,

The chamber forms a elongate chamber having a longitudinal axis.

The chamber having a first cross-sectional area at a first longitudinal position and a second cross-sectional area at a second longitudinal position, the first cross-sectional area being greater than the second cross-sectional area, Wherein the piston is at least substantially continuous between the first,

An elastically deformable material whose cross-section is adapted to conform to the cross-section of the chamber when moving from a first longitudinal position to a second longitudinal position of the chamber, and

A flat spring of a coil type having a central axis extending at least substantially along the longitudinal axis and arranged adjacent to the elastically deformable material so as to support the elastically deformable material in the longitudinal direction.

This embodiment solves the potential problem of providing only a considerable mass of elastomeric material as the piston. The fact that the material is elastic raises the problem of deformation of the piston, and when the pressure increases, the seal is lacking due to the elasticity of the material. This is especially problematic when the required dimensional change is large.

In this aspect, the elastic material is supported by a helical flat spring. The helical spring can be inflated and compressed to follow the area of the chamber, and the flat structure of the spring material ensures that the spring is not deformed by pressure.

For example, to increase the registration between the spring and the deformable material, the piston may further include a plurality of flat support means disposed between the resiliently deformable material and the spring, And the elastically deformable material.

Preferably, the support means are configured to rotate from a first position to a second position, wherein an outer boundary at the first location may be included in the first cross-sectional area, and an outer boundary at the second location may be included in the second cross-

Another aspect of the present invention relates to a combination of a piston and a chamber,

The chamber defines a elongate chamber having a longitudinal axis,

The piston being movable in the chamber from a first longitudinal position to a second longitudinal position,

The chamber having an elastically deformable inner wall along at least a portion of the inner chamber wall between the first longitudinal position and the second longitudinal position,

The chamber having a first longitudinal position and a second cross sectional area when the piston is in the first longitudinal position and a second cross sectional area when the piston is in the second longitudinal position, The cross-sectional area of the chamber between the first and second longitudinal positions is at least substantially continuously changed when the first cross-sectional area is greater than the second cross-sectional area and the piston moves between the first longitudinal position and the second longitudinal position.

Thus, as an alternative to combinations wherein the piston is shaped to accommodate changes in the cross-section of the chamber, this aspect relates to a chamber having adaptation capabilities.

Of course, the piston may be formed from at least a substantially compressible material, or the combination may be composed of a shape-adjusting piston, such as a piston according to the above-described aspects, and a shape-adjusting chamber.

Preferably, the piston is formed such that the cross-sectional shape along the longitudinal axis tapers in a direction from the first longitudinal position to the second longitudinal position.

According to a preferred method of providing a morphology regulating chamber,

An outer support structure surrounding the inner wall, and

And a fluid retained by a space formed by the outer support structure and the inner wall.

In this way, the choice of fluid or combination of fluids can aid in defining the characteristics of the chamber, such as the required force as well as the sealing between the wall and the piston.

It is clear that depending on the position in which the assembly is visible, one of the piston and the chamber may be fixed and the other may be moved, or both may be moved. This does not affect the function of the combination.

Naturally, the present combination can be used for a number of applications that focus primarily on novel methods for providing an additional way to cut the translational motion of a piston to the required / applied forces. In fact, the shape / area of the cross-section may vary along the length of the chamber to adjust the shape of the combination to a particular use and / or force. The job is to provide a pump for use by women or adolescents. Such a pump, nevertheless, should be able to provide a certain pressure. In this case, an ergonomically improved pump may be needed by determining the force that a person can provide at the location of the piston and thus provide a suitable cross-sectional shape / area to the chamber.

Another use example of such a combination is a shock absorber that determines what translational motion an area / shape requires for a given impact force. In addition, an actuator may be provided that varies the translational motion of the piston by the amount of fluid flowing into the interior of the chamber, depending on the actual position of the piston before the fluid is introduced.

In fact, the characteristics of the piston, the relative positions of the first and second longitudinal positions, and the arrangement of valves connected to the chamber can be used to determine different pressure characteristics and different force characteristics, such as pumps, motors, actuators, shock absorbers, .

In the case where the piston pump is a hand pump for tire inflation, the present invention is not limited to the case of PCT / DK96 / 00055 (including part of the continuation of the US application dated April 18, 1997), PCT / DK97 / 00223, The connector may be provided with an integral connector according to the present invention. The connectors may have integral type of pressure gauges. In a piston pump according to the present invention used as a floor pump or a &quot; carpump &quot; for inflation purposes, a pressure gauge device may be integrally formed in the pump.

For example, certain types of pistons, such as those shown in Figures 4a-4f, 7a-7e, 7j, 12a-12c, may be combined with a certain type of chamber.

For example, certain mechanical pistons, such as those shown in Figures 3A-3C, and certain composite pistons, e.g., as shown in Figures 6D-6F, and, for example, A combination of chambers of the same convex type with constant circumferential lengths may be a good combination.

Regardless of the possible circumferential length variation, for example, a combination of composite pistons as shown in Figures 9 to 12 can be used with a convex type of chamber.

The pistons of the 'umbrella type' shown in the present application have open sides, and a medium of predetermined pressure is loaded into the chamber at the opening side of the 'umbrella' shape. Also, the 'umbrella' shape portion can be operated by being rolled up and down.

Expansive pistons with a skin of a fibrous structure as shown have an internal pressure that is overpressure compared to the pressure inside the chamber. However, the internal pressure of the piston may also be equal to or lower than the pressure inside the chamber, so that the fibers are subjected to pressure instead of being subjected to tension. The resulting shape may be different from the shape shown in the figures. In this case, the load adjustment means may have to be adjusted differently, and the fibers may have to be supported. For example, the load adjustment means shown in Fig. 9d or 12b can be configured such that, for example, the movement of the piston of these means by stretching the piston rod provides a suction force on the piston, Are arranged on the other side of the holes. The shape of the piston is difficult to change, and collapse may occur. This can reduce the life span.

By these embodiments, reliable, inexpensive pumps optimized for manual operation, for example, universal bicycle pumps operated by women and adolescents, can be obtained. The shape (longitudinal and / or transverse cross-sectional shape) of the walls of the pressure chamber and / or the piston means of the pumps shown may be varied according to pump design specifications as exemplarily given. The present invention is also applicable to all types of pumps, for example multi-stage piston pumps as well as dual function pumps, piston driven by motors, for example, only the type in which the chamber or piston travels, And the chamber can both be used with pumps of the same type. Any type of media may be pumped to the piston pumps. These pumps can be used in all kinds of applications, for example pneumatic and / or hydraulic applications. And, the present invention is also applicable to pumps that are not operated manually. A reduction in applied force means a substantial reduction in energy during operation and a substantial reduction in equipment investment costs. The chambers may be produced from a tapered swage tube or the like, for example by injection molding.

In a piston pump, the medium is then sucked into a chamber which can be closed by a valve device. Such a medium is compressed by the movement of the chamber and / or the piston, and this compression medium can be displaced from the chamber by a valve. In the actuator, the medium can be forced into the chamber through the valve device and the piston and / or chamber moves to initiate movement of the attachment device. In shock absorbers, the chamber can be fully closed, and the compressible medium can be compressed within the chamber by movement of the chamber and / or the piston. In the case of incompressible media, it is provided inside the chamber, for example, the piston can be equipped with several small channels that provide dynamic friction, resulting in slower movement.

The invention can also be used in propulsion applications where a medium can be used to move a piston and / or chamber that can rotate, for example, about an axis of a motor. The above-described combinations are all applicable to the above-mentioned examples.

Accordingly, the present invention also relates to a pump for pumping a fluid,

A combination according to any one of the above aspects,

Means for matching the piston at one position outside the chamber,

A fluid inlet connected to the chamber and including valve means, and

- a fluid outlet connected to the chamber.

, The matching means may have an outer position in which the piston is in the first longitudinal position and an inner position in which the piston is in the second longitudinal position. This type of pump is preferred when a pressurized fluid is required.

In other cases, the matching means may have an outer position in which the piston is in the second longitudinal position and an inner position in which the piston is in the first longitudinal position. This type of pump is desirable when substantially no pressure is required but is required for transfer of the fluid.

When the pump is configured to be mounted upright on the floor and the piston / mating means are configured to apply a downward force to compress the fluid, such as air, the greatest force is provided ergonomically at the lowest position of the piston / mating means / . Thus, in the first case, this means that the highest pressure is provided. In the second case, this means that only the lowest position represents the largest area and hence the largest volume. However, due to the fact that the pressure exceeds the pressure required to open the valve of the tire in the tire, for example, it is possible to achieve a pressure to cause the valve to open and send a larger amount of fluid into the tire interior The smallest cross-sectional area may be preferred immediately before the lowest position of the matching means to achieve a larger cross-sectional area (Fig. 2B).

In addition, the present invention relates to a shock absorbing device,

- a combination according to any one of the combination aspects,

Means for mating with the piston at a position outside the chamber, the mating means having an outer position in which the piston is in the first longitudinal position and an inner position in which the piston is in the second longitudinal position.

The shock absorber may further include a fluid inlet connected to the chamber and including valve means.

The shock absorber may also include a fluid outlet connected to the chamber and including valve means.

It may be desirable for the chamber and the piston to form an at least substantially sealed cavity comprising a fluid and the fluid is compressed as the piston moves from the first longitudinal position to the second longitudinal position.

Usually, the shock absorber comprises means for deflecting the piston toward the first longitudinal position.

Finally, the present invention also relates to an actuator,

- a combination according to any one of the combination aspects,

Means for aligning with the piston at a position external to the chamber,

And means for introducing fluid into the interior of the chamber such that the piston is displaced between the first longitudinal position and the second longitudinal position.

The actuator may comprise a fluid inlet connected to the chamber and including valve means.

In addition, a fluid outlet connected to the chamber and including valve means may be provided.

The actuator may also include means for deflecting the piston toward the first or second longitudinal position.

The various embodiments described above are given by way of illustration only and should not be construed as limiting the invention. It will be apparent to those skilled in the art that various changes, modifications and variations in the components that may be made without departing from the true spirit and scope of the present invention, and not strictly following the preferred embodiments and examples illustrated and described herein &Lt; / RTI &gt;

All piston types, especially containers with elastically deformable walls, are sealably connected to the chamber wall during movement between longitudinal positions and may or may not be matingly connected to the walls of the chamber . Or may be connected in a mating and sealing manner to the walls of the chamber. Also, mismatches may not be made between the walls, and the walls may not contact one another, and such contact may occur, for example, when the container is moved from a first longitudinal position to a second longitudinal position within the chamber This can happen if you do.

The type of connection between the walls (the sealed condition and / or the mating condition and / or the contact and / or the no connection) is determined by the correct internal pressure inside the container wall; Can be achieved by high pressure for sealed connection, low pressure for mated connection and, for example, atmospheric pressure for a disconnected condition (production sized container), so that the container preferably has an enclosed space Since the enclosed space can control the pressure inside the container from the position outside the piston.

Another option for the mating connection is to provide a thin wall to the container which may have stiffeners that protrude from the surface of the wall such that leakage may occur between the walls of the container and the walls of the chamber.

207

According to an embodiment of the invention, a combination of a piston and a chamber is provided, the chamber defining a elongate chamber having a longitudinal axis, the chamber having a first cross-sectional area at a first longitudinal position of the chamber, Sectional area of the chamber is at least substantially continuously changed between the first and second longitudinal positions and the piston is located at a first cross-sectional area of the first And is configured to conform to the cross section of the chamber when moving from the longitudinal position to the second longitudinal position.

Preferably, the second cross-sectional area is 95% to 15% of the first cross-sectional area.

Preferably, the second cross-sectional area is 95 to 70% of the first cross-sectional area.

Preferably, the second cross-sectional area is about 50% of the first cross-sectional area.

Preferably, the piston includes a plurality of at least substantially rigid support members rotatably coupled to the common member, and elastically deformable means supported by the support members to be sealed against the inner wall of the chamber , The support member is rotatable between 10 [deg.] And 40 [deg.] Relative to the longitudinal axis.

According to an embodiment of the invention, there is also provided a combination rotatable such that the support member is at least approximately parallel to the longitudinal axis.

Preferably, the common member is attached to the handle by an operator, and the support members extend in a direction relatively away from the handle within the chamber.

Preferably, the combination further comprises means for deflecting the support members against the inner wall of the chamber.

Preferably, the piston comprises an elastically deformable container comprising a deformable material.

Preferably, the deformable material is a fluid or a mixture or foam of fluid, such as water, steam, and / or gas.

Preferably, in the cross-section through the longitudinal direction, the container has a first shape at the first longitudinal position and a second shape at the second longitudinal position, the first shape and the second shape being different.

Preferably, at least a portion of the deformable material is compressible and the area of the first shape is greater than the area of the second shape.

Preferably, the deformable material is at least substantially incompressible.

Preferably, the piston comprises a chamber in communication with the deformable container and having a variable volume.

Preferably, the volume can be changed by the operator.

Preferably, the chamber comprises a spring biased piston.

Preferably, the combination further comprises means for forming a volume of the chamber such that the pressure of the fluid inside the chamber is related to the fluid pressure between the second longitudinal position of the container and the piston.

Preferably, the forming means are configured to form in the chamber a pressure at least substantially equal to the pressure between the second longitudinal position of the container and the piston.

Preferably, the first cross-sectional shape is different from the second cross-sectional shape, and the cross-sectional shape of the chamber varies at least substantially continuously between the first longitudinal position and the second longitudinal position.

Preferably, at least 5%, preferably at least 10%, such as at least 20%, preferably at least 30%, such as at least 40%, preferably at least 50% For example at least 60%, preferably at least 70%, for example at least 80%, preferably at least 90%.

Preferably, the first cross-sectional shape is at least substantially circular and the second cross-sectional shape has a first dimension that is elongate, such as an oval, wherein the first dimension is at least twice the dimension that is at an angle to the first dimension, For at least three times, preferably at least four times.

Preferably, the first cross-sectional shape is at least substantially circular, and the second cross-sectional shape comprises at least two substantially substantially elongated portions, such as a lobe shape.

Preferably, in the cross-section at the first longitudinal position, the first circumferential length of the chamber is between 80 and 120%, for example between 85 and 115%, of the second circumferential length of the chamber in the second longitudinal cross- , Preferably 90 to 110%, for example 95 to 105%, preferably 98 to 102%.

Preferably, the first circumferential length and the second circumferential length are at least substantially equal.

Preferably, the piston is a resiliently deformable material whose cross-section is adjusted in conformity with the cross-section of the chamber when moved from the first longitudinal position to the second longitudinal position of the chamber, and at least substantially along the longitudinal axis, And a coiled flat spring disposed adjacent to the elastically deformable material to support the elastically deformable material in the longitudinal direction.

Preferably, the piston further comprises a plurality of flat support means disposed between the resiliently deformable material and the spring, the support means being rotatable along the interface between the spring and the resiliently deformable material.

Preferably, the support means may be configured to rotate from a first position to a second position, wherein in a first position, an outer boundary may be included within the first cross-sectional area, and in a second position, May be included within the cross-sectional area.

According to one embodiment of the present invention, there is provided a piston and chamber combination, wherein the chamber defines a elongate chamber having a longitudinal axis, the chamber having a first cross-sectional area at a first longitudinal position and a second cross- Wherein the first cross-sectional area is greater than the second cross-sectional area, the cross-sectional area of the chamber is at least substantially continuously varied between the first and second longitudinal positions, the piston is displaced from the first longitudinal position of the chamber The piston being configured to be adapted to the cross-section of the chamber when moving to a bi-directional position, the piston comprising: a plurality of at least substantially rigid support members rotatably coupled to the common member; And elastically deformable means supported by the support members, wherein the support members are rotated about 10 [deg.] To 40 [deg.] Relative to the longitudinal axis It is possible.

According to one embodiment, a combination is provided in which the support members are rotatable at least approximately parallel to the longitudinal axis.

Preferably, a common member is attached to a handle for use by an operator, and the support members extend in a direction relatively far from the handle within the chamber.

Preferably, the combination further comprises means for biasing the support members against the inner wall of the chamber. Wherein the chamber defines a elongate chamber having a longitudinal axis, the chamber having a first cross-sectional area at a first longitudinal position and a second cross-sectional area at a second longitudinal position, the chamber having a first cross- Sectional area of the chamber is at least substantially continuously changed between the first longitudinal position and the second longitudinal position and the piston moves from the first longitudinal position to the second longitudinal position of the chamber And the piston is configured to include an elastically deformable container including a deformable material.

Preferably, the deformable material may be a fluid or a mixture of fluids, such as water, steam, and / or gas, or a foam.

Preferably, in the longitudinally piercing cross-section, the container has a first shape in the first longitudinal direction and a second shape in the second longitudinal direction, the first shape and the second shape being different.

Preferably, at least a portion of the deformable material is compressible and the area of the first shape is greater than the area of the second shape.

Preferably, the deformable material is at least substantially incompressible.

Preferably, the piston comprises a chamber in communication with the deformable container and having a variable volume.

Preferably, the volume can be changed by the operator.

Preferably, the chamber comprises a spring biased piston.

Preferably, the combination further comprises means for forming a volume of the chamber such that the pressure of the fluid inside the chamber is related to the fluid pressure between the second longitudinal position of the container and the piston.

Preferably, the forming means are configured to form in the chamber a pressure at least substantially equal to the pressure between the second longitudinal position of the container and the piston.

Preferably, the container comprises an elastically deformable material comprising a reinforcing means.

Preferably, the reinforcing means comprises fibers.

Preferably, the foam or fluid is configured to provide a pressure higher than the highest pressure of the ambient atmospheric pressure inside the container during translational movement of the piston from the first longitudinal position to the second longitudinal position or vice versa .

Preferably, the chamber defines a elongate chamber having a longitudinal axis, the chamber having a first cross-sectional area and shape at a first longitudinal position and a second cross-sectional area and shape at a second longitudinal position, The cross-sectional shape of the chamber varies at least substantially continuously between the first longitudinal position and the second longitudinal position, and the piston moves from the first longitudinal position of the chamber to the second longitudinal position So that the cross section is adjusted in accordance with the cross section of the chamber.

Preferably, the first cross-sectional area is at least 5%, preferably at least 10%, such as at least 20%, preferably at least 30%, such as at least 40%, preferably at least 30% For example at least 60%, preferably at least 70%, for example at least 80%, preferably at least 90%.

Preferably, the first cross-sectional shape may be at least substantially circular, and the second cross-sectional shape has a first dimension that is elongate, such as an oval, wherein the first dimension is at least two times the dimension that is at an angle to the first dimension , E. G. At least three times, preferably at least four times.

Preferably, the first cross-sectional shape is at least substantially circular, and the second cross-sectional shape comprises at least two substantially substantially elongated portions, such as a lobe shape.

Preferably, in the cross-section at the first longitudinal position, the first circumferential length of the chamber is between 80 and 120%, for example between 85 and 115%, of the second circumferential length of the chamber in the second longitudinal cross- , Preferably 90 to 110%, for example 95 to 105%, preferably 98 to 102%.

Preferably, the first circumferential length and the second circumferential length are at least substantially equal.

Preferably, the piston includes a plurality of at least substantially rigid support members rotatably coupled to the common member and elastically deformable means supported by the support members to be sealed against the inner wall of the chamber .

Preferably, the piston comprises an elastically deformable container comprising a deformable material.

According to another embodiment of the present invention, there is provided a combination of a piston and a chamber, wherein the chamber defines a elongate chamber having a longitudinal axis, the chamber having a first cross-sectional area at a first longitudinal position and a second cross- Wherein the first cross-sectional area is greater than the second cross-sectional area, and the cross-sectional shape of the chamber varies at least substantially continuously between the first longitudinal position and the second longitudinal position, An elastically deformable material whose cross-section is adapted to conform to the cross-section of the chamber when moving from the directional position to the second longitudinal position, and a resiliently resilient, Including a coiled flat spring disposed adjacent an elastically deformable material to support a deformable material .

Preferably, the piston further comprises a plurality of flat support means disposed between the resiliently deformable material and the spring, the support means being rotatable along the interface between the spring and the resiliently deformable material.

Preferably, the support means are configured to rotate from a first position to a second position, wherein, in the first position, an outer boundary can be included inside the first cross-sectional area, and in the second position, Lt; / RTI &gt;

According to one embodiment of the present invention, a combination of a piston and a chamber is provided, the chamber defining a elongate chamber having a longitudinal axis, the piston moving in a chamber from a first longitudinal position to a second longitudinal position, Wherein the chamber has an elastically deformable inner wall along at least a portion of the inner chamber wall between the first longitudinal position and the second longitudinal position and wherein the chamber is configured such that the piston is disposed in the first longitudinal position Sectional area and the piston has a second cross-sectional area when the piston is disposed in the second longitudinal position and the first cross-sectional area is greater than the second cross-sectional area and the piston is moved between the first longitudinal position and the second longitudinal position Sectional area of the chamber varies at least substantially continuously between the first longitudinal position and the second longitudinal position.

Preferably, the piston is formed from an at least substantially incompressible material.

Preferably, the piston has a shape that tapers in a direction from the first longitudinal position to the second longitudinal position in the cross-section along the longitudinal axis.

Preferably, the chamber comprises an outer support structure surrounding the inner wall, and a fluid held by a space defined by the outer support structure and the inner wall.

According to one embodiment of the present invention, there is provided a pump for pumping fluid, comprising a combination according to any one of the preceding claims, means for matching the piston at a position outside the chamber, A fluid inlet including valve means, and a fluid outlet connected to the chamber.

Preferably, the matching means have an outer position in which the piston is in the first longitudinal position and an inner position in which the piston is in the second longitudinal position.

Advantageously, the matching means have an outer position in which the piston is in the second longitudinal position and an inner position in which the piston is in the first longitudinal position.

According to one embodiment of the present invention, there is provided a shock absorber, wherein the shock absorber comprises a combination as described above and means for mating with the piston at a position external to the chamber, An outer position in the directional position and an inner position in which the piston is in the second longitudinal position.

Preferably, the shock absorber further comprises a fluid inlet connected to the chamber and including valve means.

Preferably, the shock absorber further comprises a fluid outlet connected to the chamber and including valve means.

Preferably, the chamber and the piston form at least a substantially sealed cavity comprising a fluid, wherein the fluid is compressed as the piston moves from the first longitudinal position to the second longitudinal position.

Preferably, the shock absorber further comprises means for deflecting the piston toward the first longitudinal position.

According to an embodiment of the invention, there is also provided an actuator, comprising: a combination as described above; means for aligning with the piston at a position outside the chamber; and means for positioning the piston in a first longitudinal position and a second longitudinal direction And means for introducing fluid into the interior of the chamber to displace between the locations.

Preferably, the actuator further comprises a fluid inlet connected to the chamber and including valve means.

Preferably, the actuator further comprises a fluid outlet connected to the chamber and including valve means.

Advantageously, the actuator further comprises means for deflecting the piston towards the first or second longitudinal position.

Preferably, the inlet means comprise means for introducing the pressurized fluid into the chamber interior.

Preferably, the inlet means are configured to introduce a compressible fluid such as gasoline or light oil into the chamber, and the actuator further comprises means for combustion of the compressible fluid.

Preferably, the actuator further comprises a crank configured to convert the translational motion of the piston into rotational motion of the crank.

207-1

According to an embodiment of the invention, a combination of a piston and a chamber is provided, the combination comprising a elongate chamber (70) delimited by inner chamber walls (71, 73, 75) And means (76,76 ', 163), wherein the piston means includes sealing means relatively movable relative to the chamber in at least first and second longitudinal positions relative to the chamber, the chamber Having cross-sections having different cross-sectional areas at the first and second longitudinal positions of the chamber and having at least substantially continuously different cross-sectional areas at intermediate longitudinal positions between the first and second longitudinal positions, Wherein the cross-sectional area at the first longitudinal position is greater than the cross-sectional area at the second longitudinal position, and the piston means passes through the intermediate longitudinal positions of the chamber and extends from the first longitudinal position to the second longitudinal direction Sectional shapes of the chamber 162 have different cross-sectional shapes, and the cross-sectional shape of the chamber 162 is different from the cross-sectional shape of the chamber 162, The piston means 163 is also configured such that the piston means itself and the sealing means are shaped to conform to different cross-sectional shapes, and the cylinder means The first circumferential length of the cross-sectional shape of the chamber 162 is 80 to 120% of the second circumferential length of the cross-sectional shape of the chamber 162 at the second longitudinal position.

Preferably, the cross-sectional shape of the chamber 162 at the first longitudinal position is at least substantially circular, and the cross-sectional shape of the chamber 162 at the second longitudinal position is elongated, such as an oval, And the first dimension is at least two times, for example at least three times, and preferably at least four times the dimension that makes an angle with the first dimension.

Preferably, the cross-sectional shape of the chamber 162 at the first longitudinal position is at least substantially circular, and the cross-sectional shape of the chamber 162 at the second longitudinal position is at least two, such as a lobe shape Or more substantially elongated portions.

Preferably, the first circumferential length of the cross-section of the cylinder 162 at the first longitudinal position is between 85 and 115% of the second circumferential length of the cross-sectional shape of the chamber 162 at the second longitudinal position, Preferably 90 to 110%, for example 95 to 105%, preferably 98 to 102%.

Preferably, the first circumferential length and the second circumferential length are at least substantially equal.

Preferably, the cross-sectional area of the chamber at the second longitudinal position is less than or equal to 95% of the cross-sectional area of the chamber 162 at the first longitudinal position.

Preferably, the cross-sectional area of the chamber 162 at the second longitudinal position is 95% to 15% of the cross-sectional area of the chamber 162 at the first longitudinal position.

Preferably, the cross-sectional area of the chamber 162 at the second longitudinal position is between 95% and 70% of the cross-sectional area of the chamber 162 at the first longitudinal position.

Preferably, the cross-sectional area of the chamber 162 at the second longitudinal position is approximately 50% of the cross-sectional area of the chamber 162 at the first longitudinal position.

According to one embodiment of the present invention, a pump for pumping fluid is provided, the pump comprising a combination according to any of the preceding clauses, piston means (76, 163) at a position external to the chamber (162) A fluid inlet connected to the chamber and including valve means, and a fluid outlet connected to the chamber 162. The fluid outlet is connected to the chamber.

Preferably, the means for registration are arranged such that the piston means (76, 163) are at an external position in the first longitudinal position of the chamber and that the piston means (76, 163) are at an internal position in the second longitudinal position of the chamber .

Preferably, the means for matching have an external position in which the piston means (76, 163) are in the second longitudinal position and an internal position in which the piston means is in the first longitudinal position of the chamber (162).

According to an embodiment of the present invention, there is provided a shock absorber comprising: a combination according to any one of claims 1 to 9; and a mating with the piston means (76, 163) at a position outside the chamber Wherein the means for registration have an external position in which the piston means is in the first longitudinal position of the chamber (162) and an internal position in which the piston means is in the second longitudinal position.

Preferably, the shock absorber further comprises a fluid inlet connected to the chamber 162 and including valve means.

Preferably, the shock absorber further comprises a fluid outlet connected to the chamber 162 and including valve means.

Preferably, the chamber 162 and piston means 76, 163 form at least a substantially sealed cavity comprising a fluid, wherein the fluid is such that the piston means moves from a first longitudinal position of the chamber 162 to a second longitudinal position And is compressed when moving to the directional position.

Preferably, the shock absorber further comprises means for biasing the piston means toward the first longitudinal position of the chamber.

According to an embodiment of the present invention, there is also provided an actuator, comprising: a combination according to any one of claims 1 to 9; and means for aligning with the piston means at an external position of the chamber 162 And means for introducing fluid into the interior of the chamber 162 such that the piston means 76, 163 are displaced between a first longitudinal position and a second longitudinal position of the chamber.

Preferably, the actuator further comprises a fluid inlet connected to the chamber 162 and including valve means.

Preferably, the actuator further comprises a fluid outlet connected to the chamber and including valve means.

Preferably, the actuator further comprises means for biasing the piston means (76, 163) towards the first or second longitudinal position of the chamber.

Preferably, the inlet means comprise means for introducing the pressurized fluid into the interior of the chamber 162.

Preferably, the inlet means are configured to introduce a compressible fluid such as gasoline or light oil into the interior of the chamber 162, and the actuator further comprises means for combustion of the compressible fluid.

Preferably, the actuator further comprises a crank configured to convert translational motion of the piston means into rotational motion of the crank.

653

In a first aspect, the present invention relates to a combination of a piston and a chamber,

The container is formed to be elastically expandable and is formed such that the circumferential length in the no stress and unstressed state at the time of production is substantially equal to the circumferential length of the inner chamber wall of the container at the second longitudinal position.

In the present context, the cross-sections are preferably orthogonal to the longitudinal axis (= transverse).

Preferably, the second cross-sectional area is 98 to 5%, for example 95 to 70% of the first cross-sectional area. In some cases, the second cross-sectional area is about 50% of the first cross-sectional area.

A number of different techniques may be used to realize such a combination. This technique is further described in connection with the following aspects of the present invention.

According to one such technique, the piston includes a container containing a deformable material.

In this case, the deformable material may be a fluid or a mixture of fluids, such as water, steam, and / or gas, or a foam. Such materials, or some of these materials, such as gas or a mixture of water and gas, can be compressible, or at least substantially incompressible.

The deformable material may also be devices operated by spring forces, such as springs.

Thus, the container can be adjustable to provide a sealing force to the walls of the chamber having different cross-sectional areas and different circumferential lengths.

This is because the production size of the piston (unstressed, unmodified) is approximately equal to the circumferential length of the smallest cross-sectional area of the chamber cross-section and the piston expands and moves in the opposite direction when moving to a longitudinal position where the circumferential length is longer And can be accomplished by selecting to shrink.

And this can be achieved by providing means for maintaining a predetermined sealing force from the piston of the chamber wall in such a way as to maintain the piston's internal pressure at a predetermined predetermined level (s) that can be kept constant during the stroke . The pressure level of a given size depends on the difference in the circumferential lengths of the cross sections, and also on the possibility of achieving proper sealing in cross sections with the smallest circumferential length. If the difference is large and the appropriate pressure level is too high to achieve the proper sealing force in the smallest circumferential length, the pressure during the stroke may change. This requires pressure management of the piston. Commercially available materials are usually not rigid, and there is a possibility to maintain this pressure, especially if very high pressures can be used, for example by using a valve for inflation purposes. When the devices actuated by the spring force are used to obtain pressure, a valve may not be necessary.

When the cross-sectional area of the chamber changes, the volume of the container may change. Thus, in the longitudinally piercing cross-section of the chamber, the container may have a first shape in the first longitudinal direction and a second shape in the second longitudinal direction, the first shape being different from the second shape. At least in part, the deformable material is compressible and the area of the first shape is greater than the area of the second shape. In this case, the overall volume of the container will vary, so that the fluid must be compressible. Alternatively or alternatively, the piston may include an enclosed space in communication with the deformable container, the enclosed space having a variable volume. In this way, the enclosed space can fill or divert the fluid when the volume of the deformable container changes. The volume change of the container is automatically adjustable. As a result, the pressure of the container remains constant during the stroke.

The enclosure space may also include a spring biased piston. These springs can create pressure inside the piston. The volume of the enclosed space may vary. In this way, the total volume or maximum / minimum pressure of the container can be changed.

When the enclosed space is divided into the first and second enclosed spaces, these spaces are also set so that the pressure of the fluid in the first enclosed space can be related to the pressure of the fluid in the second enclosed space, Lt; RTI ID = 0.0 &gt; a &lt; / RTI &gt; The space described above may be inflatable, for example, by a valve, preferably by an expansion valve, such as a Schrader valve. For example, the possible pressure drop of the container caused by leakage through the walls of the container can be balanced by the expansion of the second enclosure space through the forming means. The forming means may be a pair of pistons, one for each enclosure.

The forming means may be configured to form at least a substantially constant pressure in the first containment space and the container during the stroke. However, the pressure level of any one type of container can be formed by the forming means; For example, if the piston is moved to have a large cross-sectional area at a first longitudinal position where the contact area at the current pressure value and / or the contact pressure may be too small to maintain proper sealing, A rise may be required. The forming means may be a pair of pistons arranged one by one in the enclosed space. The second enclosed space can be expanded to a predetermined pressure level so that the pressure rise can communicate with the first enclosed space and the container despite the fact that the container and thus the second enclosed space can be larger. This can be achieved, for example, by a combination of a piston and a chamber (second enclosed space) of a configuration in which the cross-sectional area of the piston rod changes. A pressure drop may also be desirable.

Pressure management of the piston can also be achieved by relating the pressure of the fluid inside the enclosure to the fluid pressure inside the chamber, by providing means for forming a volume of the enclosure space in communication with the chamber. In this way, the pressure of the deformable container can be varied to achieve proper sealing. For example, a simple method is to include forming means adapted to create an upward pressure on the enclosure space when the container moves from the second longitudinal position to the first longitudinal position. In this case, a simple piston can be provided between the two pressures (to prevent fluid leakage inside the deformable container).

In fact, the use of such a piston can define the relationship between the pressure values that the chamber in which the piston is translationally can be tapered in the same manner as the main chamber of the combination.

Devices that can be directly transported from the piston rod to the container can also change the volume and / or pressure of the container.

It is possible that the piston does not have or does not have an expansion valve (closed system) or it can be equipped or communicated. If the piston does not have an expansion valve, the fluid may be impermeable to the wall material of the container. In one step of the mounting process, the volume of the container is permanently closed after the fluid is injected into the volume of the piston and after being placed in the second longitudinal position of the chamber. The achievable speed of the piston may depend on considerable fluid flow possibilities which do not cause too much friction in and out of the first closed chamber. When the piston is provided with an expansion valve, the wall of the container may exhibit fluid permeability.

The container may be inflated by a pressure source contained in the piston. Alternatively, a pressure source external to the combination may be used and / or the chamber itself may be a pressure source. All solutions require piston to valve communication. Such a valve may preferably be an expansion valve, most preferably a shrouder valve, or it may be a valve having a valve core that is generally actuated by the force of a spring. The Schrader valve has a spring biased valve core pin that is closed independently of the pressure of the piston and allows all kinds of fluids to pass through the valve. However, another valve, for example, a check valve, may also be used.

The container can be expanded through the containment space when the spring biased adjusting piston acts as a check valve. The fluid may flow from the pressure source, for example an external pressure source, or, for example, from the internal pressure container, through the longitudinal ducts in the bearing of the piston rod of the spring biased piston.

When the enclosed space is divided into the first and second enclosed spaces, the expansion can be effected by the chamber as the pressure supply source, since the expansion of the second enclosed space into the first enclosed space can be prevented. The chamber may have an inlet valve provided at the bottom. In the case of expansion of the container, a valve, such as a Schrader valve, with an expansion valve, for example a valve core actuated by the force of a spring, may be used with the actuator. This may be an actuating pin according to WO 96/10903 or WO 97/43570, or it may be a valve actuator according to WO 99/26002 and US 5,094,263. The core pin of the valve moves toward the chamber when closed. The actuating pins disclosed in the above-cited WO documents have the advantage that the force for opening the valve core actuated by the force of the spring is fairly low and the expansion can be made easily by a manually operated pump. The actuators of the US patent cited above may require the force of a normal compressor.

If the operating pressure of the chamber is higher than the pressure of the piston, the piston may automatically expand.

If the working pressure of the chamber is lower than the pressure of the piston, it is necessary to achieve a higher pressure in a manner provided in the bottom of the chamber, for example, in a manner that temporarily closes the outlet valve. If the valve is, for example, a shrouder valve that can be opened by a valve actuator according to WO 99/26002, this pressure can be achieved by connecting the chamber with the space between the valve actuator and the valve core pin, By forming a detour of the substrate. This bypass can be opened (the shrouder valve can be kept closed), closed (the shrouder valve can be open) and can be achieved, for example, by a moveable piston . This movement of the piston can be done manually, for example, using a pedal. The pedal is rotated about the axis by the operator from the inactive position to the active position and vice versa. Movement of the piston may also be accomplished by other means, such as an actuator, initiated by the result of the pressure measurement of the chamber and / or the container.

Acquisition of a predetermined pressure in the container can be accomplished manually, and the operator is informed by a pressure gauge, e.g., a pressure gauge, that measures the pressure of the container. It can also be achieved automatically, for example, by the release valve of the vessel which faces the fluid when the pressure of the fluid exceeds the set maximum pressure. It can also be achieved by a cap actuated by a spring force that closes the channel from the pressure source above the valve actuator if the pressure exceeds a predetermined preset pressure value. Another solution is to open a bypass of the valve actuator according to WO 99/26002 of the shrouder valve of a container of a predetermined pressure value, as a comparable solution of a closed bypass of the outlet valve of the chamber, It may be necessary to measure the pressure inside the container to adjust the actuator to be closed.

The above-mentioned solutions are applicable to pistons comprising a container as shown in WO 00/65235 and WO 00/70227.

In this technique, the piston includes a container including an elastically deformable container wall.

The length of the section in the circumferential direction may be changed to select the stiffener which exerts the force necessary to inflate or deflate the container wall by 3 mm. Therefore, no excess material remains between the wall of the container and the wall of the chamber.

Overcoming the chamber pressure on the piston to limit the contact length (longitudinal extension) can also be achieved by selecting a suitable stiffener. The stiffener of the container wall may or may not be disposed on the container wall.

The reinforcement of the container wall may be formed of a fabric material. Although the stiffener may be one layer, it is preferably at least two layers that cross each other to facilitate mounting of the stiffener. These layers may be, for example, woven or knitted. As the weft yarns of the different layers are placed close together, the yarns may be formed of an elastic material. The layers may be vulcanized, for example, in two layers of elastic material, e.g., rubber. When the container has a production size, stress is not applied to the reinforcing material as well as the elastic material of the wall, and no deformation occurs. The expansion of the reinforcing wall of the container means that the distance between the intersections (stitch size) becomes larger as the threads expand, while the contraction means that the stitch size becomes smaller as the threads contract. Sealing of the walls of the container with respect to the walls of the chamber can be achieved by pressing the container at a predetermined pressure. As a result, the threads are slightly expanded and the stitch size becomes slightly larger. The contact of the wall of the container prevents the container from expanding due to the internal pressure to prevent the contact length from becoming larger, thereby preventing the pinching phenomenon.

The knit stiffener may be formed, for example, of an elastic thread and / or an elastically warpable thread. Expansion of the container wall can be accomplished by stretching the bending loops of the knitted fabrics. The elongation loops can return to the undeformed state when the walls of the container are contracted.

The fabric reinforcement may be produced on a production line in which the woven or knitted fabric reinforcement is placed as a cylinder inside two layers of elastic material. Inside the smallest cylinder, a bar is placed on which the caps can be moved on the bar, for example, sequentially up and down. A vulcanization oven is disposed at the end of the line. The interior of the oven may have the size and shape of the container in a non-stressed and unmodified state. Some of the cylinders located inside the oven are cut along the length so that the two caps are placed at both ends into the cylinders. The oven is closed and steam and high pressure above 100 ° C are applied. After about 1-2 minutes, the oven can be opened and two caps are vulcanized inside the finished container wall. To use a vulcanization lead time, for example, one or more ovens may be provided that rotate or translate, all of which end at the end of the production line. It may also be possible to provide one or more ovens in the production line itself using the transport lead time as the vulcanization time.

The production of the fiber reinforced walls of the container can be done in a similar manner. The reinforcing fibers can be produced, for example, by injection molding comprising an assembly socket, or by cutting a string into which both ends are inserted into the assembly socket. Both options can be easily produced consecutively. The remainder of the production process is similar to that described above for fabric stiffeners.

The piston, including the resiliently deformable container, may also include reinforcing means that are not disposed on the wall, for example, a plurality of resilient arms which may not be expanded or inflated and which are connected to the walls of the container. Where expandable, the stiffener also functions to limit deformation of the container wall due to pressure in the chamber.

Another option is a stiffener outside the container wall.

Another aspect of the invention relates to a combination of a piston and a chamber,

The chamber defines a elongate chamber having a longitudinal axis,

- the piston is movable in the chamber from at least a second longitudinal position to a first longitudinal position,

The chamber having an elastically deformable inner wall along at least a portion of the inner chamber wall between the first longitudinal position and the second longitudinal position,

The chamber has a first cross-sectional area when the piston is in the first longitudinal position and a second cross-sectional area when the piston is in the second longitudinal position, the first cross-sectional area being greater than the second cross- The cross-section of the chamber, when moved between the longitudinal position and the second longitudinal position, changes at least substantially continuously between the first longitudinal position and the second longitudinal position.

Thus, as an alternative to combinations in which the piston is shaped to accommodate changes in the cross-section of the chamber, this aspect relates to a chamber having the ability to deform.

Of course, the piston may be formed at least of a substantially incompressible material, or the combination may consist of a shape-adjusting chamber and a shape-adjusting piston, such as a piston according to the above-described aspects.

Preferably, the piston has a shape that tapers in a direction from the first longitudinal position to the second longitudinal position, in the cross-section along the longitudinal axis.

A preferred method for providing a shape-adjusting chamber is to have a chamber,

An outer support structure surrounding the inner wall, and

- a fluid held in a space defined by the outer support structure and the inner wall.

In this way, the choice of fluid or combination of fluids can aid in defining the characteristics of the chamber, such as the required force as well as the sealing between the wall and the piston.

In yet another aspect, the present invention relates to a combination of a piston and a chamber,

The chamber defines a elongate chamber having a longitudinal axis,

The chamber has a first cross-sectional shape and area at a first longitudinal position and a second cross-sectional shape and area at a second longitudinal position, the first cross-sectional shape being different from the second cross-sectional shape, Is at least substantially continuously varied between a first longitudinal position and a second longitudinal position,

The piston is configured to conform to a cross-section of the chamber when moving from a first longitudinal position to a second longitudinal position of the chamber.

This is a fairly interesting one, for example, based on the fact that different shapes of geometric shapes change the relationship between circumferential length and area. In addition, changes between the two shapes are made in a continuous manner so that the chamber has one cross-sectional shape at one location and a different cross-sectional shape at the second location, while maintaining desirable smooth variations of the chamber interior surface .

In this context, the shape of the cross section is the overall shape despite its size. Two circles have the same shape, even if they differ from one diameter to the other.

Preferably, the first cross-sectional area is at least 5%, preferably at least 10%, such as at least 20%, preferably at least 30%, such as at least 40%, preferably at least 10% For example at least 60%, preferably at least 70%, such as at least 80%, for example at least 90%.

In a preferred embodiment, the first cross-sectional shape is at least substantially circular, the second cross-sectional shape has a first dimension in the elongated shape such as an ellipsoid, and the first dimension is a dimension of the cross- At least 2 times, for example at least 3 times, preferably at least 4 times.

In another preferred embodiment, the first cross-sectional shape is at least substantially circular, and the second cross-sectional shape comprises at least two substantially at least substantially elongated portions, such as a lobe shape.

In the first longitudinal position of the cross section, the first circumferential length of the chamber is between 80 and 120%, for example between 85 and 115%, preferably between 90 and 120%, of the second circumferential length of the chamber in the second longitudinal direction of the cross- 110%, for example 95 to 105%, preferably 98 to 102%. Problems can arise when attempting to seal the wall where the dimensions change due to the fact that the sealing material must provide sufficient sealing and dimensional changes. In the case of the preferred embodiment, when the circumferential length variation is only at a low level, the sealing can be more easily controlled. Preferably, the first circumferential length and the second circumferential length are at least substantially the same so that the sealing material merely warps but does not extend to a significant degree.

As an alternative, it may be desirable for the circumferential length to slightly change during bending or deformation of the sealing material such that, for example, one side of the sealing material is compressed and another side is elongated by the bending phenomenon. Overall, it is desirable to provide the desired shape with a circumferential length that is at least close to the shape in which the sealing material is automatically "selected &quot;.

One type of piston that can be used in this type of combination includes a piston including a deformable container. The container may be elastically or inelastically deformable. In the manner described above, the walls of the container can be bent while moving within the chamber. Elastically deformable containers having a production size approximately equal to the circumferential length of the first longitudinal position of the chamber, with a type of stiffener that allows contraction by high frictional forces, can also be used in this type of combination Specifically, a high-speed piston.

Having a production size approximately equal to the circumferential length of the second longitudinal position of the chamber including the skin of the stiffener type allowing portions of the wall of the container having different distances from the central axis of the chamber in the longitudinal cross- Can also be used.

It is clear that depending on the position in which the assembly is visible, one of the piston and the chamber may be fixed and the other may be moved, or both may be moved. This does not affect the function of the combination.

The piston can also slide on the outer wall and the inner wall. The inner wall is tapered while the outer wall is cylindrical.

Naturally, the present combination can be used for a number of applications that focus primarily on novel methods for providing an additional way to cut the translational motion of a piston to the required / applied forces. In fact, the shape / area of the cross-section may vary along the length of the chamber to adjust the shape of the combination to a particular use and / or force. The job is to provide a pump for use by women or adolescents. Such a pump, nevertheless, should be able to provide a certain pressure. In this case, an ergonomically improved pump may be needed by determining the force that a person can provide at the location of the piston and thus provide a suitable cross-sectional shape / area to the chamber.

Another use example of such a combination is a shock absorber that determines what translational motion an area / shape requires for a given impact force. In addition, an actuator may be provided that varies the translational motion of the piston by the amount of fluid flowing into the interior of the chamber, depending on the actual position of the piston before the fluid is introduced.

In fact, the characteristics of the piston, the relative positions of the first and second longitudinal positions, and the arrangement of valves connected to the chamber can be used to determine different pressure characteristics and different force characteristics, such as pumps, motors, actuators, shock absorbers, .

Preferred embodiments of a combination of a chamber and a piston for use in piston pumps are described by way of example. However, in addition to the fact that the item or medium can initiate movement that can determine the type of application, i.e., the pump, actuator, shock absorber or motor, the combination is mainly a valve device in the chamber, The scope of which is not limited to the above application. In a piston pump, the medium is then sucked into a chamber which can be closed by a valve device. Such a medium can be compressed by movement of the chamber and / or the piston, and then this compression medium can be displaced from the chamber by a valve. In the actuator, the medium may be forced into the chamber through the valve device and the piston and / or chamber may move to initiate movement of the attachment device. In shock absorbers, the chamber can be fully closed and the compressible medium can be compressed by movement of the chamber and / or the piston. In the case of incompressible media, it can be provided inside the chamber, for example, the piston can be equipped with several small channels that provide dynamic friction, so that the movement can be slow.

The invention can also be used in propulsion applications where a medium can be used to move a piston and / or chamber that can rotate, for example, about an axis of a motor. Any one of the principles according to the present invention may be applicable to all of the above-mentioned examples.

The principles of the present invention may also be used for other pneumatic and / or hydraulic applications other than the piston pumps described above.

Accordingly, the present invention also relates to a pump for pumping a fluid,

A combination according to any one of the above aspects,

Means for matching the piston at one position outside the chamber,

A fluid inlet connected to the chamber and including valve means, and

- a fluid outlet connected to the chamber.

, The matching means may have an outer position in which the piston is in the first longitudinal position and an inner position in which the piston is in the second longitudinal position. This type of pump is preferred when a pressurized fluid is required.

In other cases, the matching means may have an outer position in which the piston is in the second longitudinal position and an inner position in which the piston is in the first longitudinal position. This type of pump is desirable when substantially no pressure is required but is required for transfer of the fluid.

When the pump is configured to be mounted upright on the floor and the piston / mating means are configured to apply a downward force to compress the fluid, such as air, the greatest force is provided ergonomically at the lowest position of the piston / mating means / . Thus, in the first case, this means that the highest pressure is provided. In the second case, this means that only the lowest position represents the largest area and hence the largest volume. However, due to the fact that the pressure exceeds the pressure required to open the valve of the tire in the tire, for example, it is possible to achieve a pressure to cause the valve to open and send a larger amount of fluid into the tire interior The smallest cross-sectional area may be preferred just prior to the lowest position of the matching means.

As the pump according to the present invention can use a substantially smaller operating force than comparable pumps based on conventional piston-cylinder assemblies, for example, water pumps can extract water from deeper depths. This feature is crucial, for example, in underdeveloped countries. Further, when the liquid is pumped when the pressure difference is substantially zero, the chamber according to the present invention may have another function. For example, if a pressure differential is present, it can be matched to the user's physical needs (ergonomic) by a chamber of appropriate design, for example, according to Figures 17b and 17a, respectively. This can also be achieved by the use of valves.

The present invention also relates to a piston for sealing a cylinder, and at the same time to a tapered cylinder. The piston may or may not include an elastically deformable container. The chambers thus obtained may have different circumferential sizes in cross-sectional area or may be of the same circumferential size. The piston may include one or more piston rods. The outer cylinder may be cylindrical or tapered.

In addition, the present invention relates to a shock absorbing device,

- a combination according to any one of the combination aspects,

Means for mating with the piston at a position outside the chamber, the mating means having an outer position in which the piston is in the first longitudinal position and an inner position in which the piston is in the second longitudinal position.

The shock absorber may further include a fluid inlet connected to the chamber and including valve means.

The shock absorber may also include a fluid outlet connected to the chamber and including valve means.

It may be desirable for the chamber and the piston to form an at least substantially sealed cavity comprising a fluid and the fluid is compressed as the piston moves from the first longitudinal position to the second longitudinal position.

Usually, the shock absorber comprises means for deflecting the piston toward the first longitudinal position.

The present invention also relates to an actuator,

- a combination according to any one of the combination aspects,

Means for aligning with the piston at a position external to the chamber,

And means for introducing fluid into the interior of the chamber such that the piston is displaced between the first longitudinal position and the second longitudinal position.

The actuator may comprise a fluid inlet connected to the chamber and including valve means.

In addition, a fluid outlet connected to the chamber and including valve means may be provided.

The actuator may also include means for deflecting the piston toward the first or second longitudinal position.

The invention relates to a motor comprising a combination according to any of the above-described combination aspects.

Finally, the present invention also preferably relates to a power unit (Movable Power Unit), which may for example be movable in a parachute manner. Such a unit may preferably comprise at least one set of solar cells and a power unit, for example a motor according to the invention. There may be other devices that use excess energy derived from the low operating force of at least one service device, for example a pump according to the invention and / or a device comprising a combination of a piston and a chamber according to the invention. As the arrangement of the devices according to the invention can be achieved with a lower weight than a weight based on a classical piston-cylinder combination, it may be possible to transport the MPU in a dropping manner due to a considerably lower operating force.

The various embodiments described above are given by way of illustration only and should not be construed as limiting the invention. It will be apparent to those skilled in the art that various changes, modifications and variations in the components that may be made without departing from the true spirit and scope of the present invention, and not strictly following the preferred embodiments and examples illustrated and described herein &Lt; / RTI &gt;

Containers with all piston types, especially those with elastically deformable walls, are sealably connected to the chamber wall during movement between longitudinal positions, and may be connected or not in mating alignment with the walls of the chamber have. Or may be connected in a mating and sealing manner to the walls of the chamber. Also, mismatches may not be made between the walls, and the walls may not contact one another, and such contact may occur, for example, when the container is moved from a first longitudinal position to a second longitudinal position within the chamber This can happen if you do.

The type of connection between the walls (the sealed condition and / or the mating condition and / or the contact and / or the no connection) is determined by the correct internal pressure inside the container wall; Can be achieved by high pressure for sealed connection, low pressure for mated connection and, for example, atmospheric pressure for a disconnected condition (production sized container), so that the container preferably has an enclosed space Since the enclosed space can control the pressure inside the container from the position outside the piston.

Another option for the mating connection is to provide a thin wall to the container which may have stiffeners that protrude from the surface of the wall such that leakage may occur between the walls of the container and the walls of the chamber.

653

According to one embodiment of the present invention, there is provided a piston-chamber combination, wherein the piston-chamber combination comprises a elongate chamber delimited by an inner chamber wall and comprises at least a first and a second longitudinal direction And a piston within the chamber that is moveable relative to the chamber wall in a hermetic manner relative to the chamber wall, the chambers having cross-sections with different cross-sectional areas and different circumferential lengths in the first and second longitudinal positions The cross-sections also being such that the cross-sectional areas and circumferential lengths at the intermediate longitudinal positions between the first and second longitudinal positions are at least substantially continuously different, and the cross-sectional area at the second longitudinal position and the cross- Wherein the direction length is smaller than the cross sectional area and the circumferential length at the first longitudinal position, the piston is elastically deformable, Sectional area and different circumferential lengths of the chamber while the piston is passing through the intermediate longitudinal positions of the chamber and between the first and second longitudinal positions, Wherein a circumferential length of the piston is substantially equal to a circumferential length of the chamber (162, 186, 231) in the second longitudinal position and a circumferential length of the chamber in the second longitudinal position, the container having a container wall And is produced in the same size as the production size of the container in the same non-stress-undeformed state.

Preferably, the container is inflatable, resiliently deformable, and inflatable to provide different cross-sectional areas and circumferential lengths of the piston.

Preferably, the cross-sectional area of the chamber at the second longitudinal position is in the range of 98% to 5% of the cross-sectional area of the chamber at the first longitudinal position.

Preferably, the cross-sectional area of the chamber at the second longitudinal position is in the range of 95% to 15% of the cross-sectional area of the chamber at the first longitudinal position.

Preferably, the cross-sectional area of the chamber at the second longitudinal position is approximately 50% of the cross-sectional area of the chamber at the first longitudinal position.

Preferably, the container comprises a deformable material.

Preferably, the deformable material is a fluid or a mixture or foam of fluid, such as water, steam, and / or gas.

Preferably, the deformable material comprises devices that are actuated by a spring force, such as springs.

Preferably, in the cross-section through the longitudinal direction, the container has a first shape when disposed in the first longitudinal position of the chamber, and the first shape is located in the second longitudinal position of the chamber. And is different from the second shape.

Preferably, at least a portion of the deformable material is compressible and the area of the first shape is greater than the area of the second shape.

Preferably, the deformable material is at least substantially incompressible.

Preferably, the container is inflatable with a predetermined pressure value.

Preferably, the pressure remains constant during the stroke.

Preferably, the piston includes an enclosed space communicating with the deformable container and having a variable volume.

Preferably, the volume of the enclosure space is adjustable.

Preferably, the first containment space comprises a spring biased pressure regulating piston.

Preferably, the combination further comprises means for forming a volume of the first enclosed space such that the pressure of the fluid inside the first enclosed space is related to the pressure of the second enclosed space.

Preferably, the forming means are adapted to form a pressure of the first enclosed space during the stroke.

Preferably, the forming means is adapted to form the pressure of the first enclosure space at least substantially constant during the stroke.

Preferably, the spring biased pressure regulating piston is a check valve, and the fluid of the external pressure source may flow through the check valve into the first containment space.

Preferably, the fluid from the external pressure source can be introduced into the second containment space via the expansion valve, and preferably the valve is provided with a core pin biased by a spring, such as a Schrader valve from an external pressure source do.

Preferably, the piston communicates with at least one valve.

Preferably, the piston comprises a pressure source.

Preferably, the valve is an expansion valve, and is preferably a valve having a core pin biased by a spring, such as a Schrader valve.

Preferably, the valve is a check valve.

Preferably, at least one valve is connected to the bottom of the chamber.

Preferably, the outlet valve is an expansion valve, and is preferably a valve with a spring-deflected core pin, such as a Schrader valve, which moves toward the chamber when closing the valve.

Preferably, the core pin of the valve connected to the actuator opens or closes the valve.

Preferably, the actuator is a valve actuator for actuating by valves having a valve core pin actuated by a spring force, the valve actuator comprising a housing connected to a source of pressure media, a housing inside the housing for receiving a valve to be actuated A coupling section, a cylinder surrounded by a cylinder wall having a predetermined cylinder wall diameter and having a first cylinder end and a second cylinder end located farther from the coupling section than the first cylinder end, A piston fixedly connected to an actuating pin for mating with a valve core pin actuated by a spring force of a valve received in a coupling section and a piston connected to a first piston position at a first predetermined distance from the first cylinder end Moves the pressure medium from the cylinder to the coupling section as it moves Wherein the transfer of the pressure medium between the cylinder and the coupling section is prevented when the piston is moved from the first cylinder end to the second piston position at a predetermined second distance, And wherein the piston is sealed in the cylinder wall portion in a cylinder wall portion having a predetermined cylinder wall thickness and is located in the cylinder wall, And a piston ring having a sealing edge that prevents passage of the piston to the channel and opens the channel at a first position of the piston.

Preferably, the actuator is a valve actuator for actuating by valves having a valve core pin actuated by a spring force, the valve actuator comprising a housing connected to a source of pressure media, a housing inside the housing for receiving a valve to be actuated A coupling section, circumferentially circumscribed by a cylinder wall having a predetermined cylinder wall diameter and located farther from the coupling section than the first cylinder end and the first cylinder end, and adapted to receive a pressure medium from the pressure source, A piston movably disposed within the cylinder and fixedly coupled to an actuating pin for mating with a valve core pin actuated by a spring force of a valve received in the coupling section, And wherein the piston extends from the first cylinder end And a transfer channel between the second cylinder end and the coupling section for transferring the pressure medium from the second cylinder end to the coupling section when the piston is moved to a first piston position at a predetermined first distance, Such transfer of the pressure medium between the second cylinder end and the coupling section is prevented when the piston is moved from the first cylinder end to the second piston position at a predetermined second distance, And a transmission channel having a channel portion disposed in the cylinder wall and open to the cylinder at a cylinder wall portion having the predetermined cylinder wall thickness, wherein the piston is in a sealed state with the cylinder wall portion Wherein the piston ring includes a piston ring having a sealing edge, And said second cylinder end of said second piston position to prevent said transmission of the pressure medium from said second cylinder end into the channel of said second piston position, And opens the channel with respect to the second cylinder end.

Preferably, the actuator is an actuator valve for a container-type piston pressure management system that selectively supplies pressurized air to the interior of a container-type piston, the valve comprising a cylindrical body that is open to both the pressurized fluid and the interior of the container- A valve body having a central passage of the valve body, a spring loaded check valve which is provided in the central passage to block the central passage when the valve body is closed, Wherein said valve is slidably movable from an off-position toward a check valve to an on-position and slidably received within said passageway above said check valve sliding back to the off- As a spring-loaded piston, which allows unrestricted sliding movement A spring loaded piston that mates with the surface of the central passage with sufficient spacing not so tight as to prevent leakage of pressurized fluid between the piston and the center passage surface, A piston which is movable by the piston and is compatible with a check valve to allow the passage of the pressurized fluid into the check valve and the container type piston by opening the check valve and the piston, A pressurized fluid that is axially spaced from the piston but is adjacent to the piston in an on-position and leaks through the piston as the piston moves is located between the plug and the piston So as not to delay the movement of the piston, A plug provided with a ventilation path extending from the atmosphere into the space between the piston and the plug at a ventilation point near the radial direction of the ventilation system, And a circular compression seal surrounding the vent point where the piston and plug are compressed adjacent to each other.

Preferably, the actuator is an actuator valve for a container-type piston pressure management system that selectively supplies pressurized fluid to the interior of the container-type piston, the valve being open for both the pressurized fluid and the interior of the container-type piston A valve body having a cylindrical center passageway, a spring loaded check valve housed in close proximity to the central passage to allow fluid flow during opening and to block the central passage when closed, A spring loaded piston slidably received within the passage above the check valve which slides from an off-position toward the check valve to an on-position and slides back to the off-position again when the pressurized fluid is removed; , Allowing unrestricted sliding movement A spring loaded piston which mates with the surface of the central passage with sufficient spacing not so tight as to prevent leakage of the pressurized fluid between the piston and the center passage surface as the piston moves to the on position, Type piston and to allow passage of the pressurized fluid through the check valve and the container type piston, an outer annular disk and an inner annular disk provided adjacent to the central passage, , A plug extending between the piston and the check valve, the piston extending through the stem and being spaced apart axially from the outer disk, but in an on-position adjacent to the outer disk, A leaked pressurized fluid flows from the plug An internal disk having a series of notches therein to form a vent path extending from the atmosphere into the space between the piston and the plug so as not to delay movement of the piston, An outer disc having a series of closely spaced holes in the radial direction and a compression between the piston and the plug when the piston and the plug are adjacent to each other such that pressurized air leaking through the piston when the check valve is opened is not discharged to the atmosphere And a circular compression seal surrounding said holes.

Preferably, the actuating pin for connecting to the expansion valves comprises a housing connected to the pressure source, a connection hole in the housing having an inner diameter approximately corresponding to the outer diameter of the expansion valve to which the central axis and the actuating pin are connected, Wherein the actuating pin is arranged to mate with a central core pin actuated by a spring force of the expansion valve and coaxially coaxial with the central axis and into the interior of the housing A piston having a piston disposed in the interior of a cylinder movable between a first piston position and a second piston position, and a channel, the piston portion having a first end and a second end, A piston is disposed at the first end and the channel has an opening at the first end, The first valve position being movable in the channel by a difference in forces acting on the surfaces of the valve between the first valve position and the second valve position, the opening remaining in the open position in the first valve position, The opening is closed and the upper part of the piston part forms a valve seat for the sealing surface of the valve of the valve means.

Preferably, the valve actuator is an actuating pin for connecting to the expansion valves, the valve actuator having a housing, a central axis and an external opening, a connection hole in the housing for coupling with the expansion valve, A cylinder having a cylinder wall provided with a positioning port for arranging a valve, an operating pin arranged coaxially with the coupling hole for pressing the center core pin operated by the spring force of the expansion valve, and a pressure port connected to the pressure supply source Wherein the actuating pin presses the core pin of the expansion valve at the distal end pin position when the expansion valve is positioned by the positioning means and between the proximal end pin position and the distal end pin position to be released from the core pin of the expansion valve at the proximal end pin position Wherein the operating pin is relatively movable relative to the positioning means, Wherein the piston is slidably disposed within the cylinder such that the piston is movable between a proximal piston position corresponding to the proximal end pin position and a distal piston position corresponding to the distal pin position and wherein the piston is disposed in the cylinder between the pressure port and the engagement hole, Is operable from a proximal piston position to a distal piston position by a pressure supplied from a source into the cylinder and is provided for selectively blocking or releasing the flow path between the pressure source and the engaging hole in accordance with the piston positions, At least when the expansion valve is disposed by the positioning means, the flow passage is blocked at the base piston position and released from the end piston position.

Preferably, the piston comprises means for obtaining a predetermined pressure level.

Preferably, the valve is a release valve.

Preferably, the cap actuated by the spring force closes the channel above the valve actuator when the pressure exceeds a predetermined predetermined pressure value.

Preferably, the channel is open or closed and connects the chamber with the space between the valve actuator and the core pin, the piston being movable between an open position and a closed position of the channel, and the movement of the piston And is controlled by an actuator that is adjusted accordingly.

Preferably, the channel is open or closed and connects the chamber with the space between the valve actuator and the core pin.

Preferably, a piston is movable between an open position and a closed position of the channel.

Preferably, the piston is actuated by the operator control pedal and is rotated about an axis from the inactive position to the operative position and vice versa.

Preferably, the piston is controlled by an actuator which is adjusted according to the pressure measurement result of the piston.

Preferably, the combination further comprises means for forming a volume of the enclosed space such that the pressure of the fluid in the enclosed space during the stroke is related to the pressure acting on the piston.

Preferably, the foam or fluid is provided with a pressure higher than the highest pressure of ambient atmospheric pressure inside the container during translational movement of the piston from the second longitudinal position to the first longitudinal position of the chamber or vice versa have.

Preferably, the combination comprises a pressure source.

Preferably, the pressure source has a pressure level higher than the pressure level of the container.

Preferably, the pressure source is in communication with the container by an outlet valve and an inlet valve.

Preferably, the outlet valve is an expansion valve, preferably a valve having a core pin biased by a spring, such as a shrouder valve, which moves toward the pressure source when the valve is closed.

Preferably, the inlet valve is an expansion valve, preferably a valve having a core pin biased by a spring, such as a shrouder valve, which moves towards the container when closing the valve.

Preferably, the channel is open or closed and connects the chamber with the space between the valve actuator and the core pin.

Preferably, the channel is open or closed and connects the chamber with the space between the valve actuator and the core pin.

Preferably, a piston is movable between an open position and a closed position of the channel.

Preferably, the channel is open or closed, connecting the space between the valve actuator and the core pin and the chamber through the space, the piston being movable between an open position and a closed position of the channel, And is controlled by an actuator adjusted according to a pressure level measurement result and a pressure source measurement result.

Preferably, the channel is open or closed, connecting the space between the valve actuator and the core pin and the chamber through the space, the piston being movable between an open position and a closed position of the channel, And is controlled by the actuator adjusted according to the measurement result and the measurement result of the pressure level inside the pressure source.

Preferably, the wall of the container comprises an elastically deformable material comprising reinforcing means.

Preferably, the stiffener has windings of braid angle different from 54 ° 44 '.

Advantageously, the reinforcement means comprise a fabric reinforcement that enables expansion of the container when moving to the first longitudinal position and enables shrinkage when moving to the second longitudinal position.

Preferably, the piston is produced by a production system having a plurality of vulcanized caves.

Preferably, the stiffening means comprise fibers that enable expansion of the container when it is moved to a larger, or first longitudinal position, and enable shrinkage when moved to a second longitudinal position.

Preferably, the piston is produced by a production system with a plurality of vulcanized caves, while in the production system the fibers are pushed onto the inner surface of the caps, Respectively.

Preferably, the fibers are arranged to achieve a lattice (lattice) effect.

Preferably, the reinforcement means comprises a flexible material disposed in the container and comprises a plurality of at least substantially elastic support members rotatably coupled to the common member, wherein the common members are connected to the skin of the container.

Advantageously, said members and / or common members are inflatable.

Preferably, pressure is built up on the walls of the container by means of devices actuated by a spring force.

Preferably, the piston includes a stiffener disposed outside the container.

Preferably, the container moves within the peripheral cylinder of the tapered wall.

Preferably, the chamber has a convex shape, and the operating force during the stroke is the set maximum force and tangential direction.

According to an embodiment of the present invention, there is provided a combination of a piston comprising a combination according to any of the preceding clauses or a container with a bendable wall, or a first There is also provided a combination of pistons comprising a container having a production size approximately equal to the circumferential length of the longitudinal position, wherein the cross-sections of the different cross-sectional areas have different cross-sectional shapes and the first longitudinal position and the second longitudinal position of the chamber Sectional shape of the chamber is at least substantially continuously changed and the piston is further configured so that the piston itself and the sealing means are fitted to different cross-sectional shapes.

Preferably, the cross-sectional shape of the chamber at the first longitudinal position is at least substantially circular, the cross-sectional shape of the chamber at the second longitudinal position is elongated, such as an ellipsoid, has a first dimension, Is at least two times, for example at least three times, preferably at least four times, the dimension making the angle with the first dimension.

Preferably, the cross-sectional shape of the chamber at the first longitudinal position is at least substantially circular, and the cross-sectional shape of the chamber at the second longitudinal position includes at least two substantially substantially elongated portions, such as a lobe shape do.

Preferably, the first circumferential length of the cylinder in the first longitudinal position is 80 to 120%, for example 85 to 115% of the second circumferential length of the cross-sectional shape of the chamber at the second longitudinal position, , Preferably 90 to 110%, for example 95 to 105%, preferably 98 to 102%.

Preferably, the first circumferential length and the second circumferential length are at least substantially equal.

According to one embodiment of the present invention, there is also provided a piston-chamber combination comprising a elongate chamber delimited by an inner chamber wall and a piston provided within the chamber to be moveable in a sealed manner within the chamber, Is moveable in the chamber from at least a second longitudinal position to a first longitudinal position and wherein the chamber is elastically deformable along at least a portion of the length of the chamber wall between the first longitudinal position and the second longitudinal position Wherein the piston has a first cross-sectional area when the piston is in the first longitudinal position and a second cross-sectional area when the piston is in the second longitudinal position and the first cross-sectional area is greater than the second cross- Wherein the cross-sectional shape of the chamber between the first longitudinal position and the second longitudinal position when moved between the first longitudinal position and the second longitudinal position is at least substantially And the piston comprises a resiliently expandable container having mutable geometric shapes adapted to mate with each other during the piston stroke to enable continuous sealing and wherein when the piston is placed in the second longitudinal position of the chamber, Size.

Preferably, the piston is formed at least substantially of an incompressible material.

Preferably, the piston has a tapered shape in cross-sectional shape along the longitudinal axis from the first longitudinal position to the second longitudinal position of the chamber.

Preferably, the angle between the central axis of the cylinder and the wall is at least smaller than the angle between the central axis of the chamber and the tapered wall of the piston.

Preferably, the chamber comprises an outer support structure surrounding the inner wall and a fluid retained by a space defined by the outer support structure and the inner wall.

Preferably, the space is defined by an outer structure and an inflatable inner wall.

Preferably, the piston comprises an elastically deformable container constructed according to Description 7 to 17 and comprising a deformable material.

According to one embodiment of the present invention, there is provided a pump for pumping fluid, comprising a combination according to any of the statements described at the beginning, means for matching the piston from a position outside the chamber, A fluid inlet connected to the chamber and including valve means, and a fluid outlet connected to the chamber.

Advantageously, the matching means have an external position in which the piston is in the first longitudinal position of the chamber and an internal position in which the piston is in the second longitudinal position of the chamber.

Advantageously, the matching means have an external position in which the piston is in the second longitudinal position of the chamber and an internal position in which the piston is in the first longitudinal position of the chamber.

According to an embodiment of the present invention there is provided a shock absorber comprising a combination according to any one of the preceding statements 1 to 80 and means for matching from a position outside the chamber and the piston, And an inner position in which the piston is in a second longitudinal position of the chamber.

Preferably, the shock absorber comprises a fluid inlet connected to the chamber and comprising valve means.

Preferably, the shock absorber further comprises a fluid outlet connected to the chamber and including valve means.

Preferably, the chamber and the piston form at least a substantially sealed cavity comprising a fluid, wherein the fluid is compressed as the piston moves from the first longitudinal position to the second longitudinal position of the chamber.

Preferably, the shock absorbing device further comprises means for deflecting the piston toward the first longitudinal position of the chamber.

According to an embodiment of the invention, there is provided a combination of a combination according to any one of preceding statements 1 to 80, means for aligning the piston from a position outside the chamber, a first longitudinal position and a second longitudinal position of the chamber, And means for introducing fluid into the chamber to achieve displacement of the piston between the piston and the piston.

Preferably, the actuator further comprises a fluid inlet connected to the chamber and including valve means.

Preferably, the actuator further comprises a fluid outlet connected to the chamber and comprising valve means.

Preferably, the actuator further comprises means for biasing the piston toward the first or second longitudinal position of the chamber.

Preferably, the inlet means comprise means for introducing the pressurized fluid into the chamber interior.

Preferably, the inflow means is adapted to introduce a combustion fluid such as gasoline or light oil into the interior of the chamber, and the actuator further comprises means for burning the combustion fluid.

Preferably, the inflow means are adapted to introduce inflatable fluid into the interior of the chamber, and the actuator further comprises means for inflating the inflatable fluid.

Preferably, the actuator further comprises a crank adapted to convert the translation of the piston into rotational motion of the crank.

Preferably, the motor comprises a combination according to any of the above descriptions.

Preferably, the power unit includes a combination according to any of the above descriptions, a power unit, and a power unit.

Preferably, the power unit is movable.

653-2

According to an embodiment of the present invention, there is provided a chamber comprising: a elongate chamber delimited by an inner chamber wall; and at least a first longitudinal position and a second longitudinal position of the chamber, There is provided a piston-chamber combination comprising a piston provided within a chamber, the chamber having different cross-sectional areas and different circumferential lengths at first and second longitudinal positions and between the first and second longitudinal positions Sectional areas and circumferential lengths in the intermediate longitudinal positions of the first longitudinal position have at least substantially continuously different cross-sections, wherein a cross-sectional area and a circumferential length at the second longitudinal position are greater than a cross- And wherein the piston passes through the intermediate longitudinal positions of the chamber to define a first longitudinal position and a second longitudinal position Wherein the container comprises an elastically deformable container to allow different cross-sectional areas of the piston and different circumferential lengths to be matched to different cross-sectional areas and different circumferential lengths of the chamber during relative movement of the piston between the piston And resiliently deformable to provide different cross-sectional areas and circumferential lengths, the piston communicating with a pressure source.

Preferably, the communication passage passes through an enclosed space having a variable volume.

Preferably, the communication passage penetrates the valve.

Preferably, the pressure source is in communication with the container by an outlet valve and an inlet valve.

Preferably, the outlet valve is a valve having a core pin deflected by a spring, such as an expansion valve, preferably a Schrader valve, which moves toward the pressure source when closing the valve.

Preferably, the inlet valve is a valve having a core pin biased by a spring, such as an expansion valve, preferably a Schrader valve, which moves towards the container when closing the valve.

According to one embodiment of the invention, the actuator is also provided with a valve actuator for operation by valves with a valve core pin actuated by a spring force, the valve actuator comprising a housing connected to the pressure medium supply, A coupling section inside the housing for receiving the valve, a cylinder surrounded by a cylinder wall having a predetermined cylinder wall diameter and having a first cylinder end and a second cylinder end located farther from the coupling section than the first cylinder end, A piston movably disposed within the cylinder and fixedly coupled to an actuating pin for mating with a valve core pin actuated by a spring force of a valve received in the coupling section, When the piston is moved to the first piston position at a distance, And a transfer channel for transferring the pressure medium to the turbine section, wherein when the piston is moved from the first cylinder end to a second piston position at a predetermined second distance, pressure medium transfer between the cylinder and the coupling section is prevented Wherein the second distance is greater than the first distance and the transfer channel is open to the cylinder in a cylinder wall portion disposed in the cylinder wall and having a predetermined cylinder wall thickness, the piston being fitted in a sealed state with the cylinder wall portion, And a piston ring having a sealing edge that prevents the pressure medium from being transferred to the channel at a second position of the piston and that opens the channel at a first position of the piston.

Preferably, the space between the valve actuator and the core pin and the channel connecting the chamber can be opened or closed.

Preferably, the space between the valve actuator and the core pin and the channel connecting the chamber can be opened or closed.

Preferably, a piston is movable between an open position and a closed position of the channel.

Preferably, the space between the valve actuator and the core pin and the channel connecting the chamber through the space may be open or closed, the piston being movable between an open position and a closed position of the channel, Is controlled by an actuator adjusted according to the pressure level measurement result of the pressure source and the measurement result of the pressure source.

Preferably, the space between the valve actuator and the core pin and the channel connecting the chamber through the space may be open or closed, the piston being movable between an open position and a closed position of the channel, Is controlled by an actuator adjusted according to the pressure level measurement result of the pressure of the pressure source and the measurement result of the pressure source.

Preferably, the enclosed space is the first enclosed space.

Preferably, the enclosed space is the second enclosed space.

Preferably, the first containment space comprises a spring biased pressure regulating piston.

According to one embodiment of the present invention, means are also provided for forming the volume of the first enclosed space such that the pressure of the fluid in the first enclosed space is related to the pressure of the second enclosed space.

Preferably, the spring biased pressure regulating piston is a check valve, through which the fluid of the external pressure source may flow into the first containment space.

Preferably, the fluid from the external pressure source enters the second containment space through a valve having a core pin deflected by a spring, such as an expansion valve, preferably a Schrader valve.

Preferably, the piston is produced such that the circumferential length of the piston is substantially equal to the circumferential length of the chamber in the second longitudinal position, and the production size of the container is in a stress-free unstrained state, Direction so that the piston can be expanded from the product size during relative movement of the piston from the second longitudinal position to the first longitudinal position.

Preferably, the cross-sectional area of the chamber at the second longitudinal position is in the range of 98% to 5% of the cross-sectional area of the chamber at the first longitudinal position.

Preferably, the cross-sectional area of the chamber at the second longitudinal position is in the range of 95% to 15% of the cross-sectional area of the chamber at the first longitudinal position.

Preferably, the cross-sectional area of the chamber at the second longitudinal position is approximately 50% of the cross-sectional area of the chamber at the first longitudinal position.

Preferably, the wall of the container comprises an elastically deformable material comprising reinforcing means.

Preferably, the container comprises a deformable material.

Preferably, the deformable material is a fluid or a mixture or foam of fluid, such as water, steam, and / or gas.

507

The valve actuator of the present invention and its embodiments are the subjects of Claim 1 and Claim 2 to 17, respectively. The valve connector and pressure vessel or hand pump comprising the valve actuator of the present invention are the subject matter of claims 18 and 19, respectively. Claim 20 relates to the use of a valve actuator of a predetermined configuration.

The present invention provides a valve actuator including an inexpensive combination of a cylinder in which a piston for driving an actuating pin moves and an actuating pin having a simple configuration. Such assemblies may be used in a variety of applications, such as chemical plants, where the actuating pin engages at the core pins operated by the spring force of a valve (e.g., a release valve) and valve connectors (e.g., for inflation of vehicle tires) It can be used for fixed structures. Disadvantages of conventional valve connectors have been overcome by valve actuators of the present invention. The valve actuator is characterized by a piston having a piston ring in which the piston in the first position is fitted into the cylinder at a predetermined first distance from the first end of the cylinder. In the second position of the piston, the piston is at a second predetermined distance from the first end of the cylinder, and the second predetermined distance is greater than the first predetermined distance. The cylinder wall includes a transfer channel for allowing transfer of gas phase and / or liquid medium between the cylinder and the coupling section when the piston is in the first position, The transfer of vapor and / or liquid medium between the sections is prevented by the piston.

An embodiment of the valve actuator of the present invention according to claim 6 includes an extension of the cylinder diameter disposed around the piston of the actuating fin of the cylinder bottom so that when the piston is in the first position, To a valve to be actuated from a pressure source, such that it can flow into a valve core pin actuated by an open spring force, such as a shrouder valve. The expansion of the diameter of the cylinder may be uniform or the cylinder wall may be configured such that the gap between the centerline of the cylinder and the cylinder wall is such that the gaseous phase and / or the liquid medium can freely flow around the edge of the piston ring when the piston is in the first position. And may include one cross section or several cross sections near the bottom of the cylinder where the distance increases. One variation of this embodiment includes a valve actuator device in which the diameter of the cylinder is twice that of the diameter expansion portion. The distance between the extensions may be the same as the distance between the sealing levels of the sealing means. If three different sized valves can be combined, the valve actuator may include a cylinder with three extensions. However, it may be possible to connect valves of different sizes to a valve actuator with a single device for the expansion of the diameter of the cylinder. Thus, the number of extensions may be different from the number of valves of different sizes that can be combined.

Another embodiment of the present invention according to claim 10 is characterized by a transmission channel passing through a part of the body of the valve actuator. The channels form passages for gaseous and / or liquid media between the cylinder and the portion of the valve actuator coupled to the valve. The orifice of the channel open to the cylinder is arranged such that the pressurized gas flowing from the pressure source to the cylinder when the piston is in the first position and / or the liquid medium can further flow through the channel to be operated. When the piston is in the second position, the piston blocks the cylinder so that the flow of pressurized vapor and / or liquid medium into the channel is not possible.

Instead of air, any one type of gas and / or mixture of liquids can actuate the actuating pin and can flow around the piston of the valve actuator when the piston is in the first position. The present invention can be used in all kinds of valve connectors to which a core pin (e.g., a shrouder valve) that is actuated by a spring force can be engaged regardless of the number of engagement holes or the number of engagement holes of the connector. In addition, the valve actuator may be coupled to, for example, a foot pump, a car pump, or a compressor. The valve actuator may also be integrally formed with any pressure source (e.g., a hand pump or pressure vessel) independent of the effectiveness of the securing means of the valve connector. The present invention can also be used in permanent configurations in which the actuating pin of the actuator engages with the core pin of the valve to which it is permanently mounted.

507

According to an embodiment of the present invention, there is provided a valve actuator for operation by valves having a valve core pin actuated by a spring force, the valve actuator comprising a housing connected to a source of pressure media, A cylinder surrounded by a cylinder wall having a predetermined cylinder wall diameter and having a first cylinder end and a second cylinder end located farther from the coupling section than the first cylinder end, And a piston fixedly coupled to an actuating pin for mating with a valve core pin actuated by a spring force of a valve received in the coupling section, the piston being fixed at a first predetermined distance from the first cylinder end When moved to the first piston position, the pressure from the cylinder to the coupling section Wherein a pressure medium transfer between the cylinder and the coupling section is prevented when the piston is moved from the first cylinder end to a second piston position at a predetermined second distance, And the transfer channel is open to the cylinder at a portion of the cylinder wall which is disposed in the cylinder wall and has a predetermined cylinder wall thickness and the piston is fitted in a sealed state with the cylinder wall portion, And a piston ring having a sealing edge for preventing the pressure medium from being transmitted to the channel and opening the channel at a first position of the piston.

Preferably, the first predetermined distance is greater than zero.

Advantageously, said first predetermined distance is approximately zero.

Preferably, the valve actuator includes a stopper that restricts movement of the piston at the first piston position.

Preferably, the valve actuator includes a tapered portion of the first end of the cylinder and a conical portion of the piston coincident with the tapered portion when the piston is in the first piston position.

Preferably, when the piston is in the first piston position, the pressure medium is allowed to flow freely about the periphery of the piston ring, and in the expanded position of the cylinder wall diameter, which is radially disposed about the piston when in the first piston position Thereby forming a transmission channel.

Preferably, the extension of the cylinder diameter is formed in one or a plurality of cross-sections of the circumferential surface of the cylinder wall.

Preferably, the wall of the enlarged portion includes a cylindrical enlarged portion wall portion and a sloped enlarged portion wall portion that forms an angle with the cylinder axis of greater than 0 degrees and less than 20 degrees, Wall portion and a cylinder wall portion having a predetermined cylinder wall diameter.

Preferably, the channel portion of the transfer channel is between the cylindrical extension wall portion and the coupling section, the coupling section comprises a tapered channel portion formed in the shape of a groove or a hole 107 parallel to the central axis of the cylinder, .

Preferably, the coupling section is connected to the orifice of the cylinder wall section by a transfer channel, the orifice being formed from the first cylinder end to be disposed between the piston and the second end of the cylinder when the piston is in the first piston position Distance.

Preferably, the piston is further movable to a third position and a fourth position corresponding to a predetermined third distance and a predetermined fourth distance from the first end of the cylinder in the interior of the cylinder, Wherein the predetermined distance is greater than the predetermined second distance and the predetermined fourth distance is greater than the predetermined third distance and the cylinder is located between the cylinder and the coupling section when the piston is in the third position, And a second channel for permitting delivery of the medium and for preventing the transfer of vapor and / or liquid medium between the cylinder and the coupling section when the piston is in said fourth position.

Preferably, the embodiment comprises sealing means for sealing the valve actuator on the valves of different types and / or sizes within the coupling section, the sealing means comprising a first annular sealing portion, Wherein the first annular portion is located closer to the opening of the coupling section than the second annular portion and the second annular portion is located coaxially with the central axis of the coupling section and disposed in the direction of the central axis of the coupling section, The diameter of one annular portion is larger than the diameter of the second annular portion.

Preferably, the embodiment includes a fixed thread within the coupling section for securing the valve actuator to the expansion valve.

Advantageously, said fixed thread is a temporary fixed thread.

Preferably, the cylinder wall is formed as a cylinder sleeve which is fastened and sealed within the housing and which is formed with the inclined expanding wall portion, and the cylinder sleeve extends from the first cylinder end wall portion at an angle such that the piston ring is not sealed Distance.

Preferably, the cylinder is fastened and sealed to the wall of the housing by snap-locking.

Preferably, in the embodiment, a sealing means is provided inside the coupling section for sealing the valve actuator on the valve with the valve core pin actuated by the spring force.

According to an embodiment of the present invention there is provided a valve actuator for expanding vehicle tires, comprising a valve actuator according to any one of claims 1 to 16, a valve coupled to a hand pump, foot pump, car pump, pressure vessel or compressor A connector is provided.

According to one embodiment of the present invention, a hand pump or pressure vessel for inflating a vehicle tire is also provided, wherein the valve actuator is an integral valve actuator.

According to one embodiment of the invention, the valve actuator is also provided in a fixed structure such as a chemical factory.

19597

In a first aspect, the present invention relates to a combination of a piston and a chamber, wherein the combination comprises a elongate chamber delimited by an inner chamber wall and comprises at least a first longitudinal position and a second longitudinal direction of the chamber, And a fins provided within the chamber to be moveable in a sealing manner relative to the chamber wall between the locations, the fits mating with the rigid surface to enable the movement, It is possible.

The force providing portions for enabling relative movement of the parts of the combination may be self-moving, and the aforementioned movement path does not exactly match the relative movement path of the piston rod, the piston and the chamber at any moment. Thus, the force delivering and combination system can provide flexibility at any point in the system to prevent damage. The rigid surface also provides reaction forces to the assembly to enable the relative movement to be able to align with the assembly by the changing force and also to maintain the non-movable part of the assembly towards the rigid surface Function, there can be conflicting demands on the combination. If the pump is matched to the body in a state where the pump is held down by a user's foot on a rigid surface, e.g., the floor, the above-described action may occur. In particular, when a standing person uses a floor pump to pump tires, and especially if the floor is not flat, then the combination is movable with respect to the rigid surface so that it follows the path of the force-providing portion.

In a second aspect, the chamber has cross-sections of different cross-sectional areas at a first longitudinal position and a second longitudinal position, and wherein different cross-sectional areas at intermediate longitudinal positions between the first longitudinal position and the second longitudinal position, A non-compliance is a particularly important problem when chambers whose circumferential length is at least substantially continuously varied are used. Sectional area and circumferential length at the second longitudinal position are smaller than those at the first longitudinal position. This is also effective if the cross-sectional areas at the first and second longitudinal positions have different sizes but the circumferential lengths are the same.

In one embodiment optimized for obtaining a maximum level of energy reduction, the chamber of the floor pump, for example for floor inflation, has a minimum cross-sectional area at the bottom and a maximum at the top. Thus, the force is maximized at the moment of matching the transition from the chamber to the base of the pump at the smallest cross-sectional area. Thus, the combination must be movable relative to the rigid surface to follow the path of the force-providing portion.

In a third aspect, the combination includes a base for mating the combination to a rigid surface to enable relative movement of the piston and chamber, wherein the combination is securely fastened to the base and the base is movable relative to the rigid surface Do.

The base can have three mating surfaces on the rigid surface, ensuring a stable positioning of the assembly even when the rigid surface is not even. The combination can then rotate about a line between two of the three matching surfaces. However, this approach is not desirable because the path of the human force-providing portion is a three-dimensional path. If the surface is not flat, positioning compensation of the combination may not be achieved by this solution. And, in the case of floor pumps for tire inflation, the foot of the user can press the base of the pump towards the normal rigid surface to prevent said movement (s).

In a fourth aspect, the combination comprises a base for mating the combination with a rigid surface to enable relative movement of the piston and the chamber, the combination comprising, for example, an elastically deformable bushing, It is concurrently attached to the donation.

This solution in combination with a base with three mating surfaces is an optimized solution that meets all needs, the path of the combination may be the path used by the force relief (e.g., user) The base is erected, for example, on a surface that supports the user's feet. A non-flat rigid surface can be compensated so that the non-base combination is positioned perpendicular to the water and the path can be initiated during the stroke by the use of a floor pump. After use, the combination may automatically return to the rest position, i.e., perpendicular to the rigid surface.

Of course, alternative technical solutions to the bushing are possible, for example a ball joint of the end of the cylinder held inside the base of the ball bearing. The ball may be combined with a spring that limits the deflection of the combination and restores the default deflection after use. This solution (not shown) may be more expensive than bushing.

This is also valid for piston-chamber assemblies having different circumferential lengths and different cross-sectional areas.

The guiding means may comprise a washer with a small hole into which the piston rod is suitably fitted, such washers being movable within a larger hole in the interior of the cap. The piston rod can be translated mainly in the transverse direction of the combination. The washer can be returned to its default position by a spring force, for example, an O-ring between the hole in the cap and the outside of the guide means.

The size of the holes described above determines the degree of deflection of the piston rod, as well as how much the configuration of the piston allows such deflection. When the piston rod is securely fastened to the piston, the configuration of the piston determines the degree of deflection. For example, if a ball joint is applied between the piston and the piston rod, the degree of deflection is only determined by the guide means.

In the ninth aspect, in order to allow the deflection of the piston rod in relation to the longitudinal central axis of the remaining part of the combination, the contact surfaces of the guide means are, for example, formed by the inner wall of the convex cross- Can be expressed.

In the tenth aspect, the piston may be formed in a circular shape to correspond to the movement of the piston rod, or the connection of the piston to the piston rod may be a flexible rotatable connection.

In an eleventh aspect, the present invention relates to a combination consisting of a piston and a chamber, wherein the centerline of the portions of the handle disposed opposite the center axis of the combination has an angle different from 180 °.

When operating the handle of the pump, the centerlines of the user's hands have different positions depending on how the handle is gripped by the hand (s).

In the case of classical floor pumps, high operating forces can be generated by cylinders having circular cross sections of a certain size. When no force moments occur, the hand is best positioned relative to the arm such that relatively high forces are transmitted from the user's arm through the hand connected to the arm. This is achieved when the longitudinal axis of the arm extends through the center point of the axis of the part of the handle gripped by the hand connected to the arm.

Due to the relatively large magnitude of the force, the gripping force of the hand on the handle must be robust, which can be achieved by the curvature of the hand, such as an unfolded fist: the handle design can include portions with circular cross-sections. The dimensions of the cross sections may vary depending on the distance to the center axis of the piston chamber combination.

The preferred angle between portions of the handle may be 180 [deg.] In a plane perpendicular to the central axis of the piston-chamber combination. However, the angle can also be different from 180 degrees. Also, the angle may be less than 180 degrees in a plane including the central axis. To prevent the hands from sliding off these parts, a stop may be provided, which may also be used for force transmission. As another option, of course, angles of more than 180 degrees can occur.

For innovative floor pumps with chambers having transverse cross-sections whose sizes vary between two positions of the chamber in the longitudinal direction, the forces can be low. When relatively low forces are transmitted from the user's arm through the hand connected to the arm, the hand may be positioned relative to the arm such that a predetermined force moment occurs. The contact area is provided in the unfolded hand. The handle may be configured to have a cross-section that is delimited, for example, by an elliptic curve. An axis perpendicular to the central axis of the piston-chamber combination may be larger than an axis parallel to the axis.

Preferred angles between the two portions of the handle of the plane orthogonal to the central axis of the piston-chamber combination may be slightly less than 180 degrees and slightly greater than 180 degrees (best!). These positions of the portions of the handle match the rest position (s) of the hand (s). When the knob is able to rotate about the central axis of the piston-chamber combination, both positions can be obtained by one handle design.

To prevent the presence of force moments, a line passing through the centers of both parts of the handle of the plane perpendicular to the central axis of the piston-chamber combination cuts the aforementioned axis.

In a plane containing the central axis of the piston-chamber combination, the angle may be less than 180 or may have a different value.

The conical cylinder can provide a substantial reduction in operating force. By means of a particular apparatus, the shape of the conical cylinder in the longitudinal direction of the chamber is formed so that the force on the handle is kept constant during stroke. This force may be due, for example, to the fact that the valve piston is attached to the valve seed or due to the fact that dynamic frictions occur due to the cross-sections of the small sizes of the channels, Lt; / RTI &gt; can be changed if the valve is opened later due to the forces generated by the &lt; RTI ID = 0.0 &gt; Further, due to the change in the size of the contact area, the friction of the piston against the wall of the chamber during stroke can be changed. While the shape of the cylinders shown in the longitudinal direction in all the relevant figures of this patent application is made in the manner described above, the cross-sectional views of the conical cylinder are also circular in the figures. There are geometric constraints such as the minimum size of the piston.

Accordingly, the present invention also relates to a pump for pumping a fluid,

A combination according to any one of the above aspects,

Means for matching the piston at one position outside the chamber,

A fluid inlet connected to the chamber and including valve means, and

- a fluid outlet connected to the chamber.

, The matching means may have an outer position in which the piston is in the first longitudinal position and an inner position in which the piston is in the second longitudinal position. This type of pump is preferred when a pressurized fluid is required.

In other cases, the matching means may have an outer position in which the piston is in the second longitudinal position and an inner position in which the piston is in the first longitudinal position. This type of pump is desirable when substantially no pressure is required but is required for transfer of the fluid.

When the pump is configured to be mounted upright on the floor and the piston / mating means are configured to apply a downward force to compress the fluid, such as air, the greatest force is provided ergonomically at the lowest position of the piston / mating means / . Thus, in the first case, this means that the highest pressure is provided. In the second case, this means that only the lowest position represents the largest area and hence the largest volume. However, due to the fact that the pressure exceeds the pressure required to open the valve of the tire in the tire, for example, it is possible to achieve a pressure to cause the valve to open and send a larger amount of fluid into the tire interior The smallest cross-sectional area may be desirable immediately before the lowest position of the matching means to achieve a larger cross-sectional area (see FIG. 2B).

In addition, the present invention relates to a shock absorbing device,

- a combination according to any one of the combination aspects,

Means for mating with the piston at a position outside the chamber, the mating means having an outer position in which the piston is in the first longitudinal position and an inner position in which the piston is in the second longitudinal position.

The shock absorber may further include a fluid inlet connected to the chamber and including valve means.

The shock absorber may also include a fluid outlet connected to the chamber and including valve means.

It may be desirable for the chamber and the piston to form an at least substantially sealed cavity comprising a fluid and the fluid is compressed as the piston moves from the first longitudinal position to the second longitudinal position.

Usually, the shock absorber comprises means for deflecting the piston toward the first longitudinal position.

Finally, the present invention also relates to an actuator,

- a combination according to any one of the combination aspects,

Means for aligning with the piston at a position external to the chamber,

And means for introducing fluid into the interior of the chamber such that the piston is displaced between the first longitudinal position and the second longitudinal position.

The actuator may comprise a fluid inlet connected to the chamber and including valve means.

In addition, a fluid outlet connected to the chamber and including valve means may be provided.

The actuator may also include means for deflecting the piston toward the first or second longitudinal position.

19597-1

According to an embodiment of the present invention there is provided a chamber comprising a elongate chamber delimited by an inner chamber wall and having at least a first chamber and a second chamber in a sealed state relative to the chamber wall, There is provided a piston-chamber combination comprising a piston within the chamber, wherein the combination is flexibly fastened to a base for mating the combination to a rigid surface, and wherein the combination is movable relative to the surface, It is sexually concatenated to the donation by the flexible bushing.

Preferably, an elastically flexible bushing is mounted in the hole in the base and the cylinder is mounted in the bushing hole.

Preferably, a groove cooperating with a corresponding projection on the cylinder is provided in the bushing.

Preferably, projections cooperating with corresponding grooves on the cylinder are provided in the bushing.

Preferably, the bushing includes a projection connected to the base top surface.

Preferably, the wall thickness of the bushing is greater than the wall thickness of the chamber.

Preferably, the base is provided with three mating surfaces for mating with a rigid surface.

Preferably, the chamber has different cross-sectional areas and different circumferential lengths at the first and second longitudinal positions, and the cross-sectional areas and circumferential lengths at the intermediate longitudinal positions between the first and second longitudinal positions Sectional area and circumferential length at the second longitudinal position being less than a cross-sectional area and circumferential length at the first longitudinal position, the piston means having a cross- Sectional area and different circumferential lengths of the piston during relative movement of the piston means between the first longitudinal position and the second longitudinal position through the longitudinal positions to match the different cross-sectional areas and different circumferential lengths of the chamber The dimensions can be changed to make the

Preferably, the chamber has different cross-sectional areas and the same circumferential lengths in the first and second longitudinal positions and has cross-sectional areas and circumferential lengths in the intermediate longitudinal positions between the first and second longitudinal positions Sectional area and circumferential length at the second longitudinal position being less than the cross-sectional area and circumferential length at the first longitudinal position, the piston comprising a plurality of longitudinally spaced, Sectional area and different circumferential lengths of the piston during the relative movement of the piston means between the first longitudinal position and the second longitudinal position are adapted to the different cross-sectional areas and the same circumferential lengths of the chamber, Lt; / RTI &gt;

Preferably, the piston-chamber combination is a pump comprising means for mating with the piston from a position outside the chamber, the fluid inlet comprising the valve means and the fluid outlet being connected to the chamber.

Preferably, the piston-chamber combination is a shock-absorbing device comprising means for mating with a piston from a position external to the chamber, the mating means comprising an external position in which the piston is in a first longitudinal position of the chamber, And the chamber and the piston form a sealed cavity comprising a fluid to be compressed when the piston is moved from the first longitudinal position to the second longitudinal position.

Preferably, the piston-chamber combination comprises means for matching the piston from a position outside the chamber to achieve displacement of the piston between the first longitudinal position and the second longitudinal position, And an actuator.

19597-2

According to an embodiment of the present invention there is provided a chamber comprising a elongate chamber delimited by an inner chamber wall and having at least a first chamber and a second chamber in a sealed state relative to the chamber wall, There is provided a piston-chamber combination comprising a piston within the chamber, the combination being in registration with a rigid surface, the combination including a piston rod extending through a cap for closing the end, And guided by guide means movably connected to the cap.

Preferably, the guiding means is a washer having an opening that fits around the piston rod, the washer being retained in the interior of the cap between the two surfaces, the flexible O-ring being spaced from the spaces between the surfaces and the guiding means And the cross-sectional area of the space is larger than the cross-sectional area of the O-ring.

Advantageously, said guide means comprise a convex guide surface for guiding the piston rod.

Preferably, the piston is formed in a circular shape at the connection with the wall of the chamber.

Preferably, the connection of the piston 44 to the piston rod is flexible.

Preferably, the piston-chamber combination is a pump comprising means for mating with the piston from a position outside the chamber, the fluid inlet comprising the valve means and the fluid outlet being connected to the chamber.

Preferably, the piston-chamber combination is a shock-absorbing device comprising means for mating with a piston from a position external to the chamber, the mating means comprising an external position in which the piston is in a first longitudinal position of the chamber, And the chamber and the piston form a sealed cavity comprising a fluid to be compressed when the piston is moved from the first longitudinal position to the second longitudinal position.

Preferably, the piston-chamber combination comprises means for matching the piston from a position outside the chamber to achieve displacement of the piston between the first longitudinal position and the second longitudinal position, And an actuator.

Preferably, the chamber has different cross-sectional areas and different circumferential lengths at the first and second longitudinal positions, and the cross-sectional areas and circumferential lengths at the intermediate longitudinal positions between the first and second longitudinal positions Sectional area and circumferential length at the second longitudinal position being less than the cross-sectional area and circumferential length at the first longitudinal position, the piston comprising a plurality of longitudinally spaced, Sectional area and different circumferential lengths of the piston during the relative movement of the piston means between the first longitudinal position and the second longitudinal position are adapted to different cross-sectional areas and different circumferential lengths of the chamber, Lt; / RTI &gt;

Preferably, the chamber has different cross-sectional areas and the same circumferential lengths at the first and second longitudinal positions, and the cross-sectional areas and circumferential lengths at the intermediate longitudinal positions between the first and second longitudinal positions Sectional area and a circumferential length at the second longitudinal position being less than a cross sectional area and a circumferential length at the first longitudinal position, the piston means having a cross- During the relative movement of the piston means between the first longitudinal position and the second longitudinal position through the longitudinal positions, different cross-sectional areas of the piston and different circumferential lengths are aligned with different cross-sectional areas and the same circumferential lengths of the chamber The dimensions can be changed to make the

19627
Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings.
Figure 1a shows a piston comprising a fabric reinforcement whose radial and axial dimensions are varied during a stroke according to the first embodiment, showing an initial stroke and a pressed stroke end with an uncompressed production size of the piston arrangement, and a piston with a fixed different area Lt; RTI ID = 0.0 &gt; a &lt; / RTI &gt;
1B is an enlarged view of the piston of FIG.
Figure 1c is an enlarged view of the piston of Figure 1a of the end of the stroke.
Figure 2a shows a fiber reinforcement with a wall of resilient material with radial and axial dimensions varying during stroke according to the second embodiment, showing the beginning of the stroke initiation and the end of the stroke, with the uncompressed production size of the piston arrangement, Phase effect) and a cross-section having fixed different areas.
Figure 2b is an enlarged view of the piston of Figure 2a at the beginning of the stroke.
Figure 2c is an enlarged view of the piston of Figure 2a of the end of the stroke.
Fig. 3a shows the stroke beginning and ending of a piston device with a production size, showing a piston comprising a fiber reinforcement (lattice effect) with radial and axial dimensions varying during stroke according to the third embodiment, and a piston with a fixed different Sectional view showing a chamber including cross-sections having areas.
FIG. 3B is an enlarged view of the piston of FIG.
Figure 3c is an enlarged view of the piston of Figure 3a of the end of the stroke;
Figure 3d is a top view of the piston of Figure 3a with a stiffener on the wall of the planes passing through the central axis of the piston, with the left side showing the first longitudinal position and the right side showing the second longitudinal position.
Figure 3e shows the piston of Figure 3a with a stiffener on the skin of the planes partially passing through the central axis and partially outside the central axis, with the left side showing the first longitudinal position and the right side showing the second longitudinal position. Top view.
Figure 4 shows a non-removable, inflatable piston inside a chamber with walls parallel to the central axis, in the absence of a pressure difference between the chambers between the two sides of the piston.
Fig. 5A is a view of the piston of Fig. 4 in an instantly non-moving state inside a chamber with a conical wall when the piston begins to expand and the moveable cap moves towards the non-moveable cap.
Figure 5b shows a state in which the contact area between the piston wall and the chamber wall does not momentarily move so as to increase in the second longitudinal positions of the contact area when the movable cap does not move, Fig.
Figure 5c shows that the contact area between the piston wall and chamber wall increases as the contact area between the piston wall and the chamber wall increases in the first longitudinal positions of the contact area when the movable cap does not move, Figure 5a shows the piston of Figure 5a in a state of not moving instantaneously and thus expanding so as to decrease in the second longitudinal positions.
Figure 5d is a view of the piston of Figure 5c when the non-moving cap is moved in the same direction by momentarily starting to move from the second longitudinal position to the first longitudinal position.
Fig. 5e is a view of the piston of Fig. 5d when the movement of the piston is reduced due to an increase in the contact area. Fig.
6A is a view showing an inflatable piston moving in a closed conical chamber.
Figure 6b shows an inflatable piston moving in a closed conical chamber when the chamber on both sides of the piston is in communication with the ambient atmosphere.
Figure 6C shows an inflatable piston moving in a closed conical chamber when the chamber on both sides of the piston is in communication with each other through the chamber external closing channel.
Figure 6d shows an inflatable piston moving in a closed conical chamber when the chamber on both sides of the piston communicates with each other through the piston inner closed channel.
6E shows an inflatable piston moving in a closed conical chamber when the chamber on both sides of the piston is in communication with each other through a channel between the chamber wall and the piston wall.
Figure 6f is a view of the expandable piston of Figure 6e with a duct on the contact surface of the chamber wall and the piston wall.
6G is a cross-sectional view of the piston rod of FIG. 6F seen in a first longitudinal position on the actuator piston.
Fig. 7A is an enlarged view of the piston of Fig. 1A, which is pressed at the end of the stroke, but does not move, due to the wall being parallel to the central axis;
7B is a view of the piston of Fig. 7A at a point where the center of the piston wall has a positive angle relative to the central axis so that the container moves toward the first position.
Figure 7d is a three dimensional view of a stiffener matrix of an elastic fabric material disposed on a container wall when the container is inflated.
Fig. 7E is a view showing the pattern of Fig. 6D when the container wall is inflated. Fig.
Fig. 7f is a three-dimensional view showing a reinforcement pattern of an inelastic fabric material disposed on the container wall when the piston is expanded. Fig.
Fig. 7g is a view showing the reinforcing matrix of Fig. 7f which is expanded.
8 is a view showing a combination in which the piston moves around the tapered wall in the chamber.
Fig. 9a is a perspective view of a piston device including an " octopus "type device limiting the extension of the container wall by inflatable tentacles according to the fourth embodiment, showing the beginning and end of stroke of a piston device with a production size And cross-sections having fixed different areas.
FIG. 9B is an enlarged view of the piston of FIG. 9A at the beginning of the stroke. FIG.
Figure 9c is an enlarged view of the piston of Figure 9a at the end of the stroke;
Figure 9d is a view of the piston of Figure 9a just before entering the conical portion of the chamber.
Figure 10a shows that as the pressure elliptical piston moves from the second longitudinal position to the first longitudinal position the internal volume of the piston expands and the internal volume of the piston decreases as the enclosed space has a fixed volume , The piston can change its shape into a spherical shape, the dashed lines at both ends show the outer contour of the piston, the chamber has a wall parallel to the central axis of the chamber, and in the middle, 10b can be matched to the wall of the chamber by having the same size compared to the piston of FIG. 10b, while the piston-chamber assembly shown in FIG. Fig.
Fig. 10B shows that the internal pressure of the piston is also reduced by varying the volume of the enclosed space at the first longitudinal position or the return to the second longitudinal position, thereby changing the size of the piston to prevent pinching Chamber combination of FIG. 10A in which the piston-chamber assembly is adapted to be continuously fitted to the size of the chamber.
Fig. 10c shows an alternative embodiment in which the piston is reduced in size by removing fluid from the enclosed space during its return to the first longitudinal position, which is the farthest from the first longitudinal position, or to the second longitudinal position, Lt; RTI ID = 0.0 &gt; 10a &lt; / RTI &gt; and 10b when the piston-chamber assembly is adapted to be continuously adjusted to the size of the chamber.
10D is a view showing the process of FIG. 10A as produced in a second longitudinal position when the piston is a spherical body type.
FIG. 10E is a view showing the process of FIG. 10B as produced in a second longitudinal position when the piston is a spherical body type.
Fig. 10f is a view showing the process of Fig. 10c as produced in a second longitudinal position when the piston is a spherical body type.
FIG. 10g is a view showing the process of FIG. 10a, with the exception that the size decreases as the enclosed space moves from the second longitudinal position to the first longitudinal position to reduce the use of the pressurized medium per stroke.
FIG. 10H is a view showing a process comparable to the process of FIG. 10B.
FIG. 10I is a view showing a process which is comparable to the process of FIG. 10C.
10J is a view showing the process of FIG. 10D, with the exception that the size decreases as the enclosed space moves from the second longitudinal position to the first longitudinal position to reduce the use of the pressurized medium per stroke.
FIG. 10K is a view showing a process that is comparable to the process of FIG. 10E.
FIG. 10L is a view showing a process comparable to the process of FIG. 10F.
FIG. 10m is a cross-sectional view of the motor shown in FIGS. 12a-12c with a propulsion system including an expandable expandable actuator piston rotating in a circular chamber having a pivot center axis about the center point of the motor's central axis; Fig. 1 is a view schematically showing a motor having a configuration of Fig.
10n has a propulsion system including five non-removable, expandable, expandable actuator pistons (for example) within a rotating circular chamber, the chamber having a center line coaxial with the center of rotation and having transverse cross- 13A and 13B, in which the direction lengths comprise four sub-chambers which are successively different from one another and which rotate about a main axis passing through the center of the axis.
Consumption technology
Figure 11a shows an embodiment in which the pump of the smallest size and the starter motor are all mounted on the crankshaft axis, powered by solar energy, among other equipments, inside the elongate chamber of which the cross-sectional areas and the circumferential lengths are continuously different, A pressure storage vessel, and an electric starter motor having a propulsion system including a two-stage piston pumping system and an expandable expandable actuator piston.
11B is a view schematically showing control means and pressure management for the motor of Fig. 11A.
11C is a view showing some of the actuating mechanical assemblies of the motor of FIGS. 11A and 11B when the main cylinder does not move.
11D is a view showing the pressure management of the expansion type actuator piston on the joint of the crankshaft and the connecting rod shown in Fig. 11C.
FIG. 11E is a detailed view showing the joint between the connecting rod and the piston rod shown in FIG. 11C.
FIG. 11F is a view showing in detail the structure of the channel and the crankshaft in the crankshaft shown in FIGS. 11A and 11B.
Enclosure volume technology
FIG. 11G is a cross-sectional view of a piston-and-chamber assembly of a third piston-chamber assembly for managing the pressure variation within the expandable actuator piston by varying the volume of the enclosed space through the piston of the second piston- In which the pressure regulating vessel is not regressed to pressurize the bi-directional actuator for changing the volume of the enclosed space.
11H is a view showing the configuration of FIG. 11G in which constant repressurization of the pressure storage vessel is made by the cascade pumps shown in FIG. 11A, for example.
FIG. 11I shows a state in which the speed control unit and the ESVT-pump are powered by a bidirectional actuator using a battery as a power source, and the pump for repressurizing the pressure storage vessel is powered by a separate electric motor using a battery as a power source, Individual power lines are clearly shown and at least one of the auxiliary supplies according to Figures 15A, 15B, 15C, 15E, 15F can charge the batteries, based on the concept shown in Figure &lt; 1 shows a partially actuated cylinder motor.
Fig. 11J shows two partially actuated cylinder motors based on Fig. 11i, in which each actuator piston-chamber combination has a separate speed control and an ESVT-pump and the speed controls are in communication with each other.
11J is an enlarged view of the left portion of FIG. 11J.
11Jb is an enlarged view of the right side portion of FIG. 11J.
11k shows that the ESVT-pump of the actuator piston is powered by a crankshaft powered by an electric motor powered by a battery, a speed controller (bidirectional actuator) according to one of Figs. 11h, The pump for repressurizing is powered by a separate electric motor powered by the battery, and at least one of the auxiliary power sources according to FIGS. 15A, 15B, 15C, 15E and 15F charges the batteries Lt; RTI ID = 0.0 &gt; 11h &lt; / RTI &gt;
FIG. 11L shows that one crankshaft is used for each of the ESVT-pumps for the actuator-piston assembly, the speed control portions for the actuator-piston communicate with each other, and the pump for re- Based on Fig. 11K, which is powered by a separate electric motor of Fig. 11C, in which at least one of the auxiliary supplies according to Figs. 15A, 15B, 15C, 15E, Lt; / RTI &gt; of the two cylinder motors.
11A is an enlarged view of the left part of FIG.
FIG. 11Ib is an enlarged view of the right portion of FIG.
Figure 11m shows that the ESVT-pump for the actuator piston chamber assembly is powered by the camshaft, the camshaft is driven by an electric motor powered by the battery, the speed control is a bidirectional actuator in communication with the speed regulator, The pump for repressurizing the storage vessel is powered by a separate electric motor powered by the battery and at least one of the auxiliary supplies according to Figures 15A, 15B, 15C, 15E, Lt; RTI ID = 0.0 &gt; 11h &lt; / RTI &gt;
11n shows that one camshaft is used for the ESVT-pumps for each actuator piston-chamber assembly, the speed controls for the actuator pistons communicate with each other, and the pump for re- Based on Fig. 11 (m), which is powered by a separate electric motor for charging the batteries and at least one of the auxiliary supplies according to Figs. 15A, 15B, 15C, 15E, Lt; / RTI &gt; of the two cylinder motors.
Fig. 11na is an enlarged view of the left portion of Fig. 11n.
11nb is an enlarged view of the right side portion of Fig. 11n.
Figure 11o shows that the ESVT-pump for the actuator piston-chamber is powered by the crankshaft and the crankshaft is driven by H₂H induced by electrolysis of O₂Is driven directly by an auxiliary power from a gas (e.g., air) cooling type combustion motor using a battery, and the pump for powering the pressure storage vessel is powered by the combustion motor 15d is charged by the alternator mounted on the main motor shaft, and the generated heat of the combustion motor is supplied to the speed controller by way of example Lt; RTI ID = 0.0 &gt; 11k &lt; / RTI &gt; that can be used for heating the interior of the vehicle.
Figure 11P shows that each of the ESVT-pumps for the actuator piston-chamber assembly is powered by a crankshaft, the crankshaft is driven by H₂H induced by electrolysis of O₂And the pump for re-pressurizing the pressure storage vessel is directly driven by the combustion motor, and the pump for directly pressurizing the pressure storage vessel is driven by the combustion motor, 15d are charged by the alternator mounted on the main motor shaft, and the generated heat of the combustion motor is supplied to the speed control units for the piston chamber combination by the bi-directional actuator, Lt; RTI ID = 0.0 &gt; 11O &lt; / RTI &gt; which can be used for heating the interior of a vehicle, for example.
Fig. 11Pa is an enlarged view of the left part of Fig. 11P.
FIG. 11Pb is an enlarged view of the right part of FIG. 11P.
Figure 11q shows that the ESVT-pump for the actuator piston-chamber assembly is powered by the camshaft and the camshaft is driven by H₂H induced by electrolysis of O₂(For example, an air) cooling type combustion motor by using a power source, and the electrolysis uses a battery as a power source, and a pump for re-pressurizing the pressure storage vessel is connected to the combustion motor 15d is charged by the alternator mounted on the main motor shaft, and the generated heat of the combustion motor is supplied to the electric motor Lt; RTI ID = 0.0 &gt; 11k &lt; / RTI &gt; which can be used for heating the interior of the vehicle.
Figure ll shows that each of the ESVT-pumps for the actuator piston-chamber assembly is powered by the camshaft and the camshaft is driven by H₂H induced by electrolysis of O₂(For example, an air) cooling type combustion motor by using a power source, and the electrolysis uses a battery as a power source, and a pump for re-pressurizing the pressure storage vessel is connected to the combustion motor Respectively, and the speed controllers for the actuator piston chamber assembly are powered by the bi-directional actuator and communicate with each other to power the battery, and the batteries according to Figure 15d are charged by the alternator mounted on the main motor shaft And the generated heat of the combustion motor can be used for heating the interior of the vehicle, for example.
Fig. 11 (a) is an enlarged view of a left portion of Fig. 11 (r).
Fig. 11 (r) is an enlarged view of the right part of Fig. 11 (r).
11S is a detail view of the joint of the base of the piston-chamber assembly 1061 of Figs. 11I-11R with the main axis of the motor.
Fig. 11 (t) is a view showing in detail the joint of the connecting rod of the actuator piston and the crankshaft on the main shaft of the motor according to Figs. 11 (i) to 11 (r).
Figure 11u is a detail view of the joint of the base of the piston-chamber assembly 1061 of Figures 11i-11r with the main axis of the motor.
FIG. 11V is a view showing a mechanism for driving the pumps of FIGS. 11I to 11R and a base portion thereof.
FIG. 11w is a view showing a connection joint between two crankshafts of a two-cylinder motor according to FIGS. 11j, 11l, 11n, 11p, and 11r.
Figure 11wa is a view showing an improved seal between the crankshafts of Figure 11w.
Figure 11x shows the coupling joint between two crankshafts of a two-cylinder motor in which the channels of each crankshaft are separate.
Figure 11x 'is an illustration showing improved sealing between the crankshafts of Figure 11x.
Consumption technology
Fig. 12a is a perspective view of a crankshaft shaft, in which both the pump of the smallest size and the starter motor are powered by solar energy including control means, A pressure storage vessel, and an electric starter motor with a propulsion system including a two-stage piston pumping system and an expandable expandable actuator piston rotating in a circular chamber.
Figure 12b includes an expandable inflatable actuator piston moving in a non-mobile chamber having transverse centerlines coaxial with the center of rotation, with transverse cross-sections and circumferential lengths including four successive sub- Lt; RTI ID = 0.0 &gt; 12A &lt; / RTI &gt;
12C is a schematic view of the pressure management and control means for the motor of FIG. 12B when the pressure change of the actuator piston is controlled by adding fluid to the actuator piston and removing fluid from the piston.
Enclosure volume technology
12D is a view schematically showing the pressure management and control means for the motor of Fig. 12B when the pressure change of the actuator piston is controlled by changing the volume of the enclosed space of the actuator piston.
Consumption technology
Fig. 13A shows an embodiment in which the smallest pump and the starter motor are powered by solar energy and are integrated in the crankshaft axis, in transitional chambers and circumferential lengths, A motor, a pressure storage vessel, and an electric starter motor having a propulsion system comprising at least one non-movable, expandable, expandable actuator piston of a rotary chamber having a center line coaxial with the center of rotation of the piston FIG.
13B is a view of the motor of FIG. 13A in which the piston pumps of the two-stage piston pumping system are replaced by rotary pumps mounted on the main shaft of the motor.
Figure 13c shows the ratio of the cross-sectional area and the ratio of the ratio of circumferential lengths to the ratio of the ratio of the circumferential lengths of the circumferential lengths 13A and 13B with a propulsion system including removable, expandable, expandable actuator pistons.
13D is a view schematically showing the suspension structure of the motor of Figs. 13A and 13B including the drive belt.
13E is a schematic view of the motor of FIGS. 13A and 13B, including the storage pressure vessels, when the continuously varying internal pressures of the actuator pistons are determined by separate piston-chamber assemblies for each of the computer- Pressure management and control means.
Enclosure volume technology
Fig. 13f is a schematic diagram of the embodiment of Fig. 11f, in which each piston is controlled by two piston-chamber assemblies, one of which is for continuously varying pressure and the other is for adjusting the pressure level to regulate the speed / Figure 13 illustrates the pressure management of the expandable pistons of Figure 13c in accordance with the principles.
13G is a view showing the pressing system for constitution of Fig. 13F.
Enclosure volume technology
Figure 14a shows several stages of the actuator piston which are the operating centers of the circular chamber, showing the need to change the internal pressure of the actuator piston by changing the volume below the pump piston of the connecting chamber.
14B is a view showing the configuration of Fig. 14A in which the cam wheel connected to the piston rod of the pump piston communicates with a cam of an appropriate profile.
Fig. 14C is a drawing.
Figure 14d shows that the pressure of the actuator pistons is defined by the pressure of the piston-chamber combination, the piston-chamber combination having a cam-wheel in communication with the piston, the cam- Figure 13a shows a circular moving chamber according to Figure 13a, operating on the main axis.
Fig. 14E shows the configuration of Fig. 16 (Fig. 14D) in which the configuration of Fig. 14D is constructed with an auxiliary motor shown as an electric motor rotating the cam profile and the channel including the enclosed space of the actuator piston communicates with a remote speed- Quot ;, " driven by wire ").
14F is a detail enlarged view showing a section of the piston of the circular chamber of Fig. 14E when the piston is in the first position on the circular path.
14G is a detail enlarged view showing a section of the piston of the circular chamber of FIG. 14G when the piston is in the second position on the circular path.
14H is a view showing the configuration of Fig. 14E, in which, for example, a planetary gear type gear box is constructed between the rim of the wheel and the circular chamber.
Brief Description of the Preferred Embodiments
Figure 14i illustrates a portion of a pressure management system that controls the speed of the motors when the wheels / propellers of the vehicle are cornering, for example, when they have different speeds of the wheels of the vehicle, for example, Fig.
Auxiliary supplies
15A shows a pressure storage vessel, essential components, and H (as an electrical power source) for the repressurization pump (s) for pressurizing the power lines.₂- a view showing a fuel cell.
Fig. 15B is a graph showing the relationship between the H₂And a shaft for driving an alternator for charging a battery to enable the operation of the electric motor and a combustion motor in communication with the pump (s) for re-pressurization of the pressure storage vessel.
Fig. 15C is a graph showing the relationship between H₂And a shaft for direct communication with the pump (s) through the crankshaft for re-pressurization of the pressure storage vessel.
15D is a graph showing the relationship between H₂, And a shaft for direct communication with the rotary pump (s) for re-pressurization of the pressure storage vessel.
15E is a diagram showing a capacitor charged by electricity and a power source for the electric motor (s) and communicating with the pump (s) for repressurization of the pressure storage vessel.
ESVT - Crankshaft design - multiple use of components
16A is an enlarged view of the bi-directional actuator of Figs. 11G to 11R.
16B is a diagram showing a prior study of the bi-directional actuator of FIG. 16A.
ESVT - Crankshaft design - multiple use of components
Fig. 17A is a view showing a state in which the stroke from the second longitudinal position to the first longitudinal position is the power stroke, and the stroke from the first longitudinal position to the second longitudinal position is the return stroke (nonmotor force) And two strokes of the actuator piston according to Fig. 10b.
Figure 17B shows two cylinder motors ("A") with strokes according to Figure 17a, in which the crankshaft (including two sub-crankshafts) is designed to move the power strokes of each cylinder in the opposite direction (180 °) And "B").
Figure 17c shows that the combustion motor is forced liquid cooling and one of the ESVT pumps is exchanged with the inlet / outlet for one subcrank shaft and communicates with the ESVT-pump for the other subcrankshaft and the operation is initiated by the cams of the camshaft The communication is controlled by the valve actuators according to FIG. 210E, the camshaft is driven by the combustion motor, the initial stage of the power stroke of the left cylinder is synchronized with the beginning of the return stroke of the right cylinder, FIG. 11C is a view showing two cylinder motors according to FIG. 11R, in which the second enclosed space of the shaft is separated from the third enclosed space of another sub crankshaft.
17c is an enlarged view of the left part of Fig. 17c showing the relationship of the connecting rods of both actuator pistons.
Fig. 17cb is an enlarged view of the right side of Fig. 17c.
Fig. 17D is a diagram showing the middle stage of the power stroke of the middle cylinder and the left cylinder of the return stroke of the right cylinder of the motor according to Fig. 17C.
Fig. 17d is an enlarged view of the left part of Fig. 17d showing the relationship of the connecting rods of both actuator pistons. Fig.
17D is an enlarged view of the right part of FIG. 17D.
17E is a diagram showing the end of the return stroke of the right cylinder and the end of the power stroke of the left cylinder of the motor according to Fig. 17D.
17Ea is an enlarged view of the left portion of FIG. 17e, showing the relevance of the connecting rods of the two actuator pistons.
17E is an enlarged view of the right side of FIG. 17E.
Fig. 17F is a diagram showing the initial stages of the power stroke of the right cylinder of the motor according to Fig. 17E and the return stroke of the left cylinder. Fig.
Figure 17fa is an enlarged view of the left portion of Figure 17f showing the relevance of the connecting rods of both actuator pistons.
Fig. 17fb is an enlarged view of the right side of Fig. 17f.
Fig. 17G is a diagram showing the middle stage of the power stroke of the right cylinder and the middle stage of the return stroke of the left cylinder of the motor according to Fig.
Fig. 17ga is an enlarged view of the left portion of Fig. 17g showing the relationship of the connecting rods of both actuator pistons.
17Gb is an enlarged view of the right side of FIG. 17g.
FIG. 17H is a diagram showing the end of the power stroke and the end of the return stroke of the left cylinder of the motor according to FIG. 17G. FIG.
17H is an enlarged view of the left part of FIG. 17H showing the connection rods of both actuator pistons.
17Hb is an enlarged view of the right side of FIG. 17H.
ESVT - Crankshaft design - multiple use of components
Figure 18A shows a cross-sectional view of two cylinder motors ("A ") with strokes according to Figure 17A, in which a crankshaft (including two sub-crankshafts) is designed to move the power strokes of each of the actuator pistons in the same direction "And" B ").
18A (L) is an enlarged view of the left portion of FIG. 18A showing the relationship of the connecting rods of both actuator pistons.
18A (R) is an enlarged view of the right side of FIG. 18A.
Figure 18b shows that the combustion motor is a forced liquid cooling type and comprises one ESVT-pump acting as both actuator pistons, the second enclosure space of one subcrank shaft communicating with the third enclosure space of the other subcrankshaft FIG. 17C is a view showing a simple configuration of two cylinder motors according to FIG. 17C. FIG.
18B is an enlarged view of the left portion of FIG. 18B showing the relationship of the connecting rods of both actuator pistons.
Fig. 18Bb is an enlarged view of the right part of Fig. 18B.
18c is a diagram showing the middle stages of the power strokes of the left and right cylinders of the motor according to Fig. 18b.
Fig. 18ca is an enlarged view of the left portion of Fig. 18c showing the relationship of the connecting rods of both actuator pistons. Fig.
Fig. 18cb is an enlarged view of the right side of Fig. 18c.
18D is a diagram showing the end stages of the power strokes of the left and right cylinders of the motor according to Fig. 18C.
Fig. 18d is an enlarged view of the left part of Fig. 18d showing the connection rods of both actuator pistons. Fig.
18db is an enlarged view of the right side of FIG. 18d.
Fig. 18E is a diagram showing the initial stages of the return stroke of the left and right cylinders of the motor according to Fig. 18D. Fig.
Figure 18ea is an enlarged view of the left portion of Figure 18e, showing the relevance of the connecting rods of both actuator pistons.
Fig. 18eb is an enlarged view of the right side of Fig. 18e.
Fig. 18F is a diagram showing the middle stage of the return stroke of the left and right cylinders of the motor according to Fig. 18E.
Fig. 18fa is an enlarged view of the left part of Fig. 18f showing the relationship of the connecting rods of both actuator pistons.
Fig. 18fb is an enlarged view of the right side of Fig. 18f.
FIG. 18G is a diagram showing the end stages of the return stroke of the left and right cylinders of the motor according to FIG.
Fig. 18ga is an enlarged view of the left portion of Fig. 18g showing the relationship of the connecting rods of both actuator pistons.
18gb is an enlarged view of the right side of Fig. 18g.
CT - Crankshaft design - multiple use of components
19A shows that some components are additionally operated, and the auxiliary power is H₂H &lt; / RTI &gt;₂11B and 11C, which are combustion motors for burning a single cylinder motor.
FIG. 19B is a cross-sectional view in which the third enclosed spaces (outlets) are disposed at the center line of the connecting portion so as to communicate with each other through the connecting portions of the two sub crankshafts, 19A, in which the crankshaft (including the two sub-crankshafts) is simultaneously moved in the same direction (0 DEG) (synchronized) in accordance with the principle of FIG. 18A by the power strokes of each actuator piston Fig. 2 is a view showing two cylinder motors.
19B is an enlarged view of the left portion of FIG. 19B.
Fig. 19Bb is an enlarged view of the right portion of Fig. 19B. Fig.
Fig. 19c is a cross-sectional view in which comparative enclosed spaces (here, third enclosed spaces) are connected to each other via sub-crankshafts, and the second enclosed spaces together communicate with the outside (check valve) (Including shafts) move in the same direction (180 degrees) (asynchronous) according to the principle of Figure 18A, with the power strokes of each of the actuator pistons being based on Figure 19a.
Fig. 19cca is an enlarged view of the left part of Fig. 19c.
Fig. 19cb is an enlarged view of the right part of Fig. 19c.
19620
Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings.
21A is a longitudinal section view of a conical chamber having constant maximum operating force characteristics of the pump showing common (pressure) boundaries and convex and concave shapes of the sides of the longitudinal cross-sections between the boundaries.
FIG. 21B is a diagram showing the shape (broken line) of the chamber (overpressure of 10 bar) of FIG. 21A and another chamber (overpressure of 16 bar) of the same chamber length.
Figure 22 is a longitudinal section of the conical chamber of Figure 21 showing the expansion chamber continuous with the chamber.
Figure 23 shows a progressive conical chamber with constant maximum operating force characteristics of the pump showing a specific internal concave transition from the inner conical portion to the inner linear portion of the chamber at the second longitudinal positions parallel to the central axis of the chamber. Fig.
Figure 24 is an illustration of an inflatable deformable piston that does not move itself from a second longitudinal position to a first longitudinal position because the inner wall of the chamber of Figure 23 is parallel to the central axis;
25 is a view showing a chamber of a certain type having a hose nipple as an outlet connected to the hose.
19630 Brief description of drawings
In the following, preferred embodiments of the invention will be described with reference to the drawings.
Fig. 32A is a view showing the circular chamber of Fig. 12B, showing the movement of the piston in the non-moving chamber. Fig.
Fig. 30B is a view showing the circular chamber of Figs. 13C and 14D, in which the piston does not move and the chamber moves. Fig. Here, the design of the circular chamber and the sub-chambers is identical to that of FIG. 30A.
Fig. 31A is a view showing Fig. 14D, wherein a cross section X-X is shown.
FIG. 31B shows an enlarged detail view of the section X-X of the chamber of FIG. 31A.
Mathematical Explanation for Circular Chamber and Piston
Figure 32a shows the walls and orthogonal planes of the chamber to the base circle intersections in a circle whose center is at the bas circle.
32B is a sectional view of a boundary portion of the piston.
Figure 32c shows the geometry of the cap, with reference to formulas (2.1) and (2.2) for the area and internal volume of the cap for which only the values of a and h are required, .
Figure 32d shows a piston with end caps.
Figure 32E shows the piston with end caps inside a transparent Fermi-tube chamber.
Figure 32f shows the pure contact area between the piston and the chamber, which can be seen in the transparent chamber wall.
Figure 32g shows the surface area between the piston and the chamber.
Figure 32h shows a cross-section of the chamber wall; the chamber reaction force is marked gray; and the total force on the cross-section is orthogonal to the chamber wall, which results in the cross-section being in the longitudinal (variable) Because the force is proportional to the internal pressure of the cylinder.
Figure 32i shows the cross section of Figure 32h, with an additional cross-section for providing an open view.
Fig. 32J shows Fig. 32H, and the red vector is a component of the gray force along the longitudinal direction.
Figure 32k shows Figure 32j, with additional cross-section for providing an open view.
Figure 32l shows Figure 32j, in which the actual sliding force along the wall is shown in blue - this is obtained by projecting a red vector orthogonal to the chamber wall.
Figure 32m shows Figure 32l, with an additional cross-section for providing an open view.
19640 Brief description of drawings
In the following, preferred embodiments of the invention will be described with reference to the drawings.
Figure 40a is a longitudinal cross-sectional view of a pump having a piston comprising a support means, an O-ring and a flexible impervious layer in a first longitudinal position, wherein the flexible impermeable layer is supported by a foam do.
Figure 40b is a detail view of the suspension of the vulcanized, support means, O-ring and flexible impermeable layer together.
40C is a longitudinal cross-sectional view of the piston of Fig. 40A in a second longitudinal position;
41A is a plan view of the piston of FIG. 40A and a cross-sectional view of the chamber from a first longitudinal position;
Fig. 41B is a detailed view of the suspension on the supporting means of the O-ring and the lying spring of the piston of Fig. 40A.
Figure 41c shows a cross-sectional view of the chamber with the piston of Figure 40a in a second longitudinal position.
Figure 41d shows a bottom view of the piston of Figure 40a, and a cross-sectional view of the chamber in the first longitudinal piston, showing the spiral reinforcement of the impermeable sheet.
FIG. 41E shows a bottom view of the piston of FIG. 40A, and a cross-sectional view of the chamber in the first longitudinal piston, illustrating the spiral reinforcement of the impermeable sheet.
42A is a longitudinal cross-sectional view of a pump having a piston including a support means, an O-ring, and a flexible impermeable layer at a first longitudinal position, wherein a central axis of the flexible impermeable layer chamber It accomplishes.
42B is a detail view of suspension of the support means, O-ring and flexible impermeable layer, which are vulcanized together.
42C is a longitudinal sectional view of the piston of Fig. 42A at the second longitudinal position.
19650 Brief description of drawings
Figure 50 shows a top view of the suspension of a foam piston, in particular reinforcing pins.
Figure 51 shows a longitudinal section A-A of a piston made of PU foam.
Figure 52 shows a longitudinal section B-B of the piston of Figure 50;
19650-1 Brief description of the drawing
In the following, preferred embodiments of the invention will be described with reference to the drawings.
55A shows a piston in a first longitudinal piston of an advanced pump, wherein the piston includes a metal pin, the metal pin is fastened in a rotational direction relative to the holder plate of the holder by a magnetic force, The holder plate is mounted on the piston rod.
55B shows an enlarged longitudinal section P-P of the holder plate mounted on the holder.
Figure 55c shows an enlarged view of the holder plate on the holder from Figure 55b.
Figure 55d shows an enlarged view of the protuberance in the recess between the holder and the holder plate for improved squeeze of the impermeable layer.
Figure 55E illustrates an alternative solution for reinforcement and fastening of the foam to that shown in Figures 55A-D.
Figure 55f shows an enlarged view of the holder plate on the holder from Figure 55e.
Figure 55g shows a solution to the automatic clockwise rotation of the reinforcing pin of the foam when the piston is actuated towards the first longitudinal position.
Figure 55h shows an enlarged view of the holder plate on the holder from Figure 55g.
19660 Brief description of drawings
Figure 60 shows longitudinal and cross-sectional views of the ends of a container type piston.
Fig. 61 shows details of both ends of the container type piston of Fig. 60. Fig.
Figure 62 shows a container type piston at the beginning and end of stroke in a chamber with constant force on the piston rod (see 19620).
19660-2 Brief description of the drawing
In the following, preferred embodiments of the invention will be described with reference to the drawings.
63 is a view showing the forces from the actuator piston to the wall of the longitudinal chamber.
Figure 64a shows an elliptical type piston in the chamber with a longitudinal central axis at a 20 [deg.] Angle.
Figure 64b shows an elliptical type piston in the chamber with a longitudinal central axis at a 10 [deg.] Angle.
19680-2 Brief description of the drawing
In the following, preferred embodiments of the invention will be described with reference to the drawings.
80a shows a chamber of a pump according to section 19620, with a piston according to section 19680 at three different longitudinal positions, the piston wall comprising a separate rotatable part, Is adapted to the inclination of the walls of the chamber and their surfaces are sealingly connected to the walls of the chamber and the piston wall.
80B shows an enlarged detail view of the contact area when the piston is in the first longitudinal position.
80c shows an enlarged detail of the contact area when the piston is in the second longitudinal position.
Fig. 80d shows the separated portion when the piston is in the second longitudinal position. Fig.
Fig. 80E shows an alternative spherical shape of the separating portion of that shown in Figs. 80A-C.
80f shows an alternative semicircular shape of the separating portion of that shown in Figures 80a-c when the piston is in the second longitudinal position, the separating portion is vulcanized (enlarged) on the piston It is processed.
80g illustrates the piston according to FIG. 80f, wherein the separating portion is disposed below the line through the longitudinal intermediate point of the flexible wall of the piston.
80h illustrates the piston according to FIG. 80c, wherein the separating portion is disposed below the line through the longitudinal midpoint of the flexible wall of the piston.
80i illustrates the piston of Fig. 80j in a second longitudinal position of the chamber according to section 19620. Fig.
Figure 80j shows an enlarged view of the piston of Figure 80i as produced.
81a shows a chamber of a pump according to section 19620, with an inflatable piston according to section 19680 at three different longitudinal positions, the wall of the piston being adapted to the inclination of the wall of the chamber, Surfaces are sealingly connected to the walls of the chamber and the piston wall.
81B shows an enlarged detail view of the contact area when the piston is in the first longitudinal position.
81C shows an enlarged detail of the contact area when the piston is disposed between the first and second longitudinal positions.
81D shows a piston (enlarged) in which the piston is disposed in a second longitudinal position.
Figure 82a shows a chamber of a pump according to section 19620, with an inflatable piston according to section 19680 at three different longitudinal positions, the wall of the piston comprising two parts with different circumferences, The largest of the two portions includes a contact area between the wall of the chamber and the wall of the piston.
82B shows an enlarged detail view of the contact area when the piston is in the first longitudinal position.
82c shows an enlarged detail of the contact area when the piston is disposed between the first and second longitudinal positions.
Figure 82d shows a piston (enlarged) in which the piston is disposed in a second longitudinal position.
Figure 83a shows the piston of Figure 82d, including the piston rod, which is not inflated.
83B shows the piston of FIG. 83A in its expanded, first longitudinal position.
83c shows the piston of Fig. 83b, with the clamp in the piston rod holding the piston in place when retracted.
83D shows the piston of FIG. 83C when the foam is inserted through the enclosed space of the piston rod.
83E shows the piston of FIG. 83D, which is unclamped after the foam is inserted and cured.
83f shows the piston of FIG. 83e on a second longitudinal position with a pressure sensor and an expansion valve.
83g shows an enlarged view of the pressure sensor and the expansion valve of the piston of Fig. 83e.
Figure 83h shows the piston of Figure 83e on the second longitudinal position, with pressure sensors and expansion valves of other types than those shown in Figures 83f or 83g.
Figure 83i shows an enlarged view of the pressure sensor and the expansion valve of the piston of Figure 83h.
Figure 83j shows the piston of Figure 83e on the second longitudinal position, with pressure sensors and expansion valves of other types than those shown in Figures 83f, 83g, or 83h.
83K shows an enlarged view of the pressure sensor and the expansion valve of the piston of FIG. 83J.
84A shows the piston of FIG. 83H for small size applications, for example, wherein the pulling spring provides an expansion force for the piston wall, other than the force induced from the inflatable toroid, The pressure side of the pump piston has a foam inside to communicate with the space and to maintain expansion of the part properly under external pressure.
84b shows an improved piston on the basis of Fig. 84a with separate channels assembled on the inside of the foam and piston walls within the entire piston, the piston being connected to a venting hole And the channel communicates with the space enclosed by the piston.
84c shows the piston of Fig. 84a, wherein the low pressure side of the wall of the piston is a flat cone.
Figure 84d shows a spherically shaped piston on the second and first longitudinal position of the chamber with the separated portion on the outer wall as shown in Figures 80f, 80g, 80j for an elliptical type piston.
84e shows a spherically shaped piston with a piston wall, which piston includes two parts with different circumferences, the largest part being the chamber and the piston wall (also see Fig. 82a-c for elliptical piston types, d), while the piston is shown in the second and first longitudinal positions.
Fig. 84f shows a spherical piston having an expandable toroid as a separate part, as shown in Fig. 84b for an oval shaped piston.
19690-2 Brief description of the drawing
In the following, preferred embodiments of the invention will be described with reference to the drawings.
A single moving piston in the chamber
90A shows a rotary piston in a circular chamber, wherein the piston is connected to the axle by a connecting rod, and the axle and connecting rod communicate with each other including the channel.
90B shows an enlarged view of the details of assembling the connecting rod and the axle, and the teeth between the axle and the connecting rod.
Fig. 90c shows an enlarged view of the connecting rod on which the piston is mounted, based on Fig. 14f when the piston is disposed in the first circular position. Fig.
Fig. 90d shows an enlarged view of the connecting rod on which the piston is mounted, based on Fig. 14g when the piston is disposed in the second circular position. Fig.
With CT and / or ESVT-system
90E shows the configuration of Fig. 90A, wherein the channels in the axle communicate with the CT-pressure management system according to Figs. 11A and 11D for the joint of the connecting rod to the axle.
90f shows the configuration of Fig. 90a, wherein the channels in the axle communicate with the ESVT-pressure management system according to Figs. 11g and 11t for the joint of the connecting rod to the axle.
90g shows the configuration of Fig. 90a, wherein the channels in the axle communicate with the ESVT-pressure management system according to Figs. 11i and 11t for the joint of the connecting rod to the axle.
90h shows a preferred embodiment based on the configuration of FIG. 90g in the combination of camshafts, which controls the timing of the ESVT-system, while the energy is H₂Lt; RTI ID = 0.0 &gt; H &lt; / RTI &gt;₂ Which is driven by a combustion motor.
A plurality of moving pistons (simultaneously in a circular position)
90i shows four moving pistons in the chamber, and the space in the piston communicates with the enclosed space in each connecting rod in communication with the enclosing space of the axle, in which the piston moves around.
90j shows an enlarged view of the joint between the connecting rods and the axle of Fig. 90i.
ESVT - with system
90k shows the configuration of Fig. 90i, wherein the channel in the axle communicates with the ESVT-pressure management system according to Fig. 11i, and with a joint based on Figs. 11t and 90j.
901 shows a preferred embodiment based on the configuration of FIG. 90k in the combination of camshafts, which controls the timing of the ESVT-system, while the energy is H₂Lt; RTI ID = 0.0 &gt; H &lt; / RTI &gt;₂ Which is driven by a combustion motor.
A single moving chamber around the piston
91A shows a rotating circular chamber in which a piston is disposed, wherein the piston is connected to an axle by a connecting rod, the axle and connecting rod comprising a channel.
91b is an enlarged view of the detail of the assembling of the connecting rod and axle of Fig. 91a, with the bearing between the axle and the connecting rod and the channels communicating with each other in the middle - this configuration is preferably combined with the CT system .
The same combinations may be possible in CT and / or ESVT- systems as shown for Figures 90k-90l (inclusive).
91c shows cross-sections of the hubs including the connecting rod and axle channels and the bearings with the holes and the teeth and grooves for fixing the position of the non-moving piston.
91d shows cross sections as shown in FIG. 91 wherein the rotation of the bearing is provided by the rotation of the hub of the spokes of the chamber.
91E shows a cross section of a hub comprising connecting rods and axle channels, wherein the reduced axle diameter provides a constant communication between the chambers 19619-EP.
The plurality of rotating pistons in the parallel chambers
92a shows a three-cylinder motor in which the pistons rotate about a main central axis - the chambers are interconnected and a gear box is mounted on the assembly, the main axle of which is connected to the main center axle of the pistons Communicating - this configuration can be combined with the ESVT - system preferably.
92b shows the three cylinder motors of Fig. 92a, on which a variable pitching wheel is assembled on each side of the motor on which to communicate relative to the comparable pitching wheels on the wheel axle of the vehicle, (low) pitch mode (Variomatic^®): A low speed is shown, and such a configuration would preferably be combined with an ESVT-system.
92c is the same as FIG. 92b, wherein the pitches of the wheels are opposite (: high speed).
A plurality of moving chambers for transmitting torque on the central axis
93a shows a three-cylinder motor in which the chambers rotate, the torque is transmitted to the main center axis, and the external gearbox communicates with the axle, which can preferably be combined with the ESVT system There will be.
93B shows an enlarged view (4: 1) of the left edge of the building up of the central axis of the motor.
207 Brief description of drawing
In the following, preferred embodiments of the invention will be described with reference to the drawings.
BRIEF DESCRIPTION OF THE DRAWINGS The invention will be described in detail below with reference to the figures and drawings. The following is illustrated in the figures and figures, wherein the transverse cross section refers to the cross section perpendicular to the direction of movement of the piston and / or chamber, while the longitudinal cross section is along the direction of the direction of movement:
Figure 100 shows a so-called indicator plot of a one-stage single working piston pump having a piston and cylinder with a constant diameter.
Figure 102a shows an indicative chart of a piston pump according to the invention, wherein part (A) shows the option of moving the piston while part (B) shows the option of moving the chamber.
Figure 102b shows an indicator plot of a pump according to the invention, wherein the transverse cross section is increased again from a certain point in the pump stroke by the still increasing pressure.
103a shows a longitudinal cross section of a pump with pistons having radially-axially varying dimensions during the stroke and different regions of the cross-section of the pressure chamber; And at the end (first embodiment).
Figure 103 (b) shows an enlarged view of the piston arrangement of Figure 103 (a) at the beginning of the stroke.
Figure 103 (c) shows an enlarged view of the piston arrangement of Figure 103 (a) at the end of the stroke.
Figure 103d shows a longitudinal cross-section of a chamber of a floor pump according to the invention with dimensions in which the operating force is kept substantially constant - the comparison of a conventional low pressure cylinder (dotted line) with a high pressure floor Are simultaneously shown.
104a shows a longitudinal cross section of a pump with a piston having a fixed cross-section of the cross-section of the pressure chamber and a piston with dimensions varying radially-axially in the course of the stroke, the piston arrangement being arranged at the beginning of the pump stroke And is shown at the end (second embodiment).
Figure 104 (b) shows an enlarged view of the piston arrangement of Figure 104 (a) at the beginning of the stroke.
Figure 104 (c) shows an enlarged view of the piston arrangement of Figure 104 (a) at the end of the stroke.
Figure 104d shows section A-A of Figure 104b.
Figure 104E shows cross section B-B of Figure 104C.
Figure 104f illustrates an alternative solution to the loading portion of Figure 104d.
105a shows a longitudinal cross section of a pump having a piston with a fixed cross-section of the cross-section of the pressure chamber and a piston with dimensions varying radially-axially in the course of the stroke, the piston arrangement being arranged at the beginning of the pump stroke And is shown at the end (third embodiment).
Figure 105 (b) shows an enlarged view of the piston arrangement of Figure 105 (a) at the beginning of the stroke.
Fig. 105C shows an enlarged view of the piston arrangement of Fig. 105A at the end of the stroke.
Figure 105d shows a cross-section C-C of Figure 105a.
Fig. 105E shows a cross section D-D of Fig. 105A.
Figure 105f shows the pressurization chamber of Figure 105a with piston means having sealing means made of composite materials.
Figure 105g shows an enlarged view of the piston means of Figure 105f during the stroke.
Figure 105h shows an enlarged view of the piston means of Figure 105f at the end of the stroke, both while still under pressure and no longer under pressure.
106a shows a longitudinal cross section of a pump with a fourth embodiment of a piston having fixed different regions of the transverse cross section of the pressure chamber and varying radially-axially in the course of the stroke, the piston arrangement At the beginning and end of the pump stroke.
Figure 106 (b) shows an enlarged view of the piston arrangement of Figure 106 (a) at the beginning of the stroke.
Figure 106c shows an enlarged view of the piston arrangement of Figure 106a at the end of the stroke.
Figure 106d shows a fourth embodiment of the pressure chamber and piston of Figure 106a with radially-axially varying dimensions during the stroke, the piston arrangement being shown at the beginning and end of the pump stroke.
Fig. 106E shows an enlarged view of the piston arrangement of Fig. 106D at the beginning of the stroke.
Fig. 106F shows an enlarged view of the piston arrangement of Fig. 106D at the end of the stroke.
107a shows a longitudinal cross-section of a pump comprising a sixth embodiment of a piston having a recessed wall of a pressure chamber with fixed dimensions and a radially-axially varying dimension during a stroke, the piston arrangement comprising: At the beginning and end of the pump stroke.
Figure 107 (b) shows an enlarged view of the piston arrangement of Figure 105 (a) at the beginning of the stroke.
Figure 107c shows an enlarged view of the piston arrangement of Figure 105a at the end of the stroke.
Figure 107d shows a cross section E-E of Figure 107b.
Figure 107E shows the cross section F-F of Figure 107C.
Figure 107f shows examples of transverse cross sections created by Fourier series expansions of the pressurizing chamber, where the cross-sectional area (cross-sectional area) is reduced while the circumferential size remains constant.
107g shows a modification of the pressurizing chamber of Fig. 107a, the pressurizing chamber now having a fixed transverse direction designed in such a way that the area is reduced during the pump stroke while its circumference remains approximately constant or is reduced to some extent And has a longitudinal cross section having a cross section.
Figure 107h shows the transverse cross section G-G (dotted lines) and the longitudinal cross section H-H of Figure 107g.
Figure 107i shows the cross section G-G (dotted lines) and longitudinal section I-I of Figure 107h.
Fig. 107J shows a modification of the piston of Fig. 107B in cross section H-H of Fig. 107H.
Figure 107k shows other examples of cross-sectioned cross sections created by Fourier series expansions of the pressurizing chamber, where the cross-sectional area is reduced while the circumferential periphery size remains constant.
Figure 107L shows an example of an optimized convex shape of a transverse section under certain constraints.
Figure 107m shows an example of an optimized non-convex shape of the transverse section under certain constraints.
Figure 108a shows a longitudinal cross-section of a pump comprising a seventh embodiment of a piston having a convex portion of the wall of the pressurizing chamber with fixed dimensions and a radial direction-axially varying dimension during stroke; At the beginning and end of the pump stroke.
Figure 108 (b) shows an enlarged view of the piston arrangement of Figure 105 (a) at the beginning of the stroke.
Figure 108 (c) shows an enlarged view of the piston arrangement of Figure 105 (a) at the end of the stroke.
109a shows a longitudinal cross-section of a pump comprising an eighth embodiment of a piston with fixed different regions of the transverse cross section of the pressurizing chamber and with radially-axially varying dimensions during the stroke, At the beginning and end of the pump stroke.
109B shows an enlarged view of the piston arrangement of FIG. 109A at the beginning of the stroke.
Figure 109c shows an enlarged view of the piston arrangement of Figure 109a at the end of the stroke.
Figure 109d shows the piston of Figure 109b with a different tuning arrangement.
Figure 110a shows a ninth embodiment of a piston similar to the piston of Figure 109a with fixed different regions of the cross-section of the pressure chamber.
110B shows an enlarged view of the piston arrangement of FIG. 110A at the beginning of the stroke.
Fig. 110C shows an enlarged view of the piston arrangement of Fig. 110A at the end of the stroke.
111a shows a longitudinal cross section of a pump comprising a tenth embodiment of a piston with fixed different regions of the transverse cross section of the pressurizing chamber and with radially-axially varying dimensions during the stroke, the piston arrangement At the beginning and end of the pump stroke.
FIG. 111B shows an enlarged view of the piston arrangement of FIG. 111A at the beginning of the stroke.
FIG. 111C shows an enlarged view of the piston arrangement of FIG. 111A at the end of the stroke.
Figure 112a shows a longitudinal cross section of a pump comprising an eleventh embodiment of a piston with fixed different regions of the transverse cross section of the pressurizing chamber and dimensions varying radially and axially during the stroke, At the beginning and end of the pump stroke.
112B shows an enlarged view of the piston arrangement of FIG. 112A at the beginning of the stroke.
Fig. 112C shows an enlarged view of the piston arrangement of Fig. 112A at the end of the stroke. Fig.
Figure 113a shows a longitudinal cross section of a pump comprising a piston with variable different areas of the transverse cross section of the pressure chamber and a fixed geometrical shape sizes, the arrangement of which is at the beginning of the pump stroke and at the end Respectively.
113B shows an enlarged view of the arrangement of the assemblies at the beginning of the pump stroke.
Figure 113c shows an enlarged view of the arrangement of the assemblies during the pump stroke.
Figure 113d shows an enlarged view of the arrangement of the combinations at the end of the pump stroke.
Figure 114 shows a longitudinal cross section of a pump comprising a piston with variable different regions and variable geometrical shape sizes of the cross section of the pressurizing chamber, the arrangement of which is at the beginning of the pump stroke, Lt; / RTI &gt;
653 Brief description of drawing
In the following, preferred embodiments of the invention will be described with reference to the drawings.
Figure 201a shows a longitudinal cross-section of a non-moving piston in a non-pressurized cylinder at a first longitudinal position, the piston being shown at its production size and in a pressurized condition.
Figure 201b shows the contact pressure of the pressurized piston of Figure 201a on the wall of the cylinder.
Figure 202a shows a longitudinal section of the piston of Figure 201a in the cylinder at the first (right) and second (left) longitudinal position, and the piston is non-pressurized.
Figure 202b shows the contact pressure of the piston of Figure 202a on the wall of the cylinder in the second longitudinal position.
Fig. 202c shows the contact pressure of the piston of Fig. 202a in the cylinder at the second longitudinal position, which is pressurized to the same pressure level as the pressure level of Fig. 201a - and also the first longitudinal position Are also shown.
Figure 202d shows the contact pressure of the piston of Figure 202c on the wall of the cylinder at the second longitudinal position.
Figure 203a shows a longitudinal section of the piston of Figure 201a in the cylinder in a first longitudinal position, shown in production size and being pressurized while the piston is exposed to pressure in the chamber.
Figure 203 (b) shows the contact pressure of the piston of Figure 203 (a) on the wall of the cylinder.
Figure 204a shows a longitudinal cross-section of a non-moving piston in accordance with the invention in a non-pressurized cylinder at a second longitudinal position, shown in its production size and pressurized to a certain level.
Figure 204b shows the contact pressure of the pressurized piston of Figure 204a on the wall of the cylinder.
Figure 204c shows a longitudinal cross-section of the non-moving piston in the cylinder at a second longitudinal position, shown in a first longitudinal position, at a production size and when pressed to the same level as figure 204a .
Figure 204d shows the contact pressure of the piston of Figure 204c on the wall of the cylinder.
Figure 205a shows a longitudinal section of the piston of Figure 204a in a cylinder that is non-pressurized at a second longitudinal position when the piston is at a product size and when it is pressurized.
Figure 205b shows the contact pressure of the piston of Figure 205a on the wall of the cylinder.
Figure 205c shows a longitudinal section of the piston of Figure 204a in the cylinder at a second longitudinal position, where the piston is at its product size and is pressurized and exposed to pressure from the cylinder.
Figure 205d shows the contact pressure of the piston of Figure 205c on the wall of the cylinder.
206a shows a longitudinal section of a first embodiment of a piston comprising a chamber with fixed different regions of the cross-section in cross-section and a textile reinforcement with radially-axially-varying dimensions during the stroke, the press- The piston arrangement is shown at the beginning and end of the pump stroke - not pressurized in production size.
Figure 206b shows an enlarged view of the piston of Figure 206a at the beginning of the stroke.
Figure 206c shows an enlarged view of the piston of Figure 206a at the end of the stroke.
Figure 206d shows a three-dimensional view of a reinforcing matrix of elastic textile material disposed within a wall of the container when the container is about to expand.
FIG. 206E shows the pattern of FIG. 206D when the wall of the container is inflated.
Figure 206f shows a three-dimensional view of the reinforcing matrix of the inelastic textile material disposed within the walls of the container when the piston is about to expand.
Figure 206g shows the pattern of Figure 206f when the wall of the container is inflated.
Figure 206h shows the production detail of the piston with the textile reinforcement.
FIG. 207a is a cross-sectional view of a second portion of a piston including a chamber having fixed different regions of transverse cross-sections and a fiber reinforcement having radially-axially-varying dimensions of the elastomeric material of the wall during stroke ('lattice effect' The piston arrangement is shown at the beginning and at the end of the pump stroke, which is shown in the longitudinal section of the embodiment and which is not depressurized at its production size.
Figure 207b shows an enlarged view of the piston of Figure 207a at the beginning of the stroke.
Figure 207c shows an enlarged view of the piston of Figure 207a at the end of the stroke.
208a shows a chamber having fixed different regions of transverse cross-sections with different circumferential lengths and a fiber reinforcement (without a &quot; lattice effect &quot;) having radially-axially-varying dimensions of the elastic material of the wall during travel, - the piston arrangement is shown in a first longitudinal position and - in a second longitudinal position, which is not pressurized - at its production size.
Figure 208b shows an enlarged view of the piston of Figure 208a at the beginning of the stroke.
Figure 208c shows an enlarged view of the piston of Figure 208a at the end of the stroke.
Figure 208d shows a top view of the piston of Figure 208a with reinforcement in the wall in planes through the central axis of the piston, which is to the left in the first longitudinal position and to the right in the second longitudinal position.
Figure 208e shows a top plan view of a piston similar to the piston of Figure 208a with reinforcement in the wall in the plane through the central axis of the piston and the partially outer side, which is the left side at the first longitudinal position and the right side at the second longitudinal position Respectively.
Figure 208f shows a top view of a piston similar to the piston of Figure 208a with reinforcement in the wall in planes that do not pass through the central axis of the piston, which is to the left in the first longitudinal position and to the right in the second longitudinal position.
Figure 208g shows the production details of the piston with fiber reinforcement.
Figure 209a includes an "octopus" device, which restricts the stretching of the container wall by tentacles, which can be inflated and a chamber having fixed different regions of transverse cross-sections with different peripheral perimeter lengths In which the piston arrangement is shown in a first longitudinal position of the chamber and in a second longitudinal position in which it is not pressurized - in its production size.
Figure 209b shows an enlarged view of the piston of Figure 209a in a first longitudinal position of the chamber.
Figure 209c shows an enlarged view of the piston of Figure 209a at a second longitudinal position of the chamber.
210A shows the embodiment of FIG. 206, wherein the pressure inside the piston is changed by a Schrader valve, for example disposed in the handle and / or by expansion through a check valve in, for example, a piston rod And the space enclosed therein balances the change in the volume of the piston during the stroke.
210b illustrates a bushing that enables connection to an external pressure source instead of an expansion valve.
210c shows a detailed portion of the guide portion of the rod of the check valve.
210d shows the flexible piston of the check valve in the piston rod.
210E illustrates the embodiment of FIG. 206, wherein the volume of the enclosed space of FIGS. 210A-D to inflate the piston from a pressure source comprises a pressure source and inlet valve, and an outlet valve And an enlarged view of the details of the valve-valve actuator combinations according to Figure 211d.
FIG. 210f shows the embodiment of FIG. 10e, wherein there are steerable valves and jet or nozzle-black boxes.
Figure 211a shows the embodiment of Figure 206 wherein the pressure inside the piston can be kept constant during the stroke and wherein the second enclosed space can be inflated through the shrouder valve disposed in the handle, The piston communicating with the first enclosed space through the arrangement, the piston being inflated by a valve actuator arrangement having a chamber pressure as a shrouder valve + pressure source, and the outlet valve of the chamber being manually controlled by a rotatable pedal .
Figure 211b shows a piston arrangement and its bearings wherein the piston arrangement communicates between the second and first containment spaces.
Figure 211c shows an alternative piston arrangement that is self-adapting to a cross-sectional area that varies in its longitudinal direction within the piston rod.
Figure 211d shows an enlarged view of the expansion arrangement of the piston of Figure 211a at the end of the stroke.
Figure 211E shows an enlarged view of the bypass arrangement for the valve actuator for closing and opening the outlet valve.
Figure 211f shows an arrangement of the automatic closing and opening arrangement of the outlet valve and a comparable system for obtaining a predetermined pressure in the piston (dashed line) is shown.
Figure 211g shows an enlarged view of the expansion arrangement of the piston of Figure 211a and includes a combination of a valve actuator and a spring-force operated cap, which allows the piston to automatically expand from a chamber to a predetermined predetermined pressure .
Figure 211h shows an alternative solution to the solution of Figure 211g and includes a combination of a valve actuator and a spring disposed under the piston of the valve actuator.
212 shows an arrangement in which the pressure in the container can depend on the pressure in the chamber.
Figure 213a shows a longitudinal cross-section of a piston with a resilient or flexible wall having different regions of transverse cross-sections and a piston with fixed geometric-shaped dimensions, the arrangement of which is at the beginning and end of the pump stroke Respectively.
Figure 213b shows an enlarged view of the arrangement of the combinations at the start of the pump stroke.
Figure 213c shows an enlarged view of the arrangement of the combinations during the pump stroke.
Figure 213d shows an enlarged view of the arrangement of the assemblies in the feed of the pump stroke.
214 shows a longitudinal cross-section of a piston having a resilient or flexible wall with different regions of transverse cross-sections and a piston with variable geometric-shaped dimensions, the arrangement of which permits the initiation, Lt; / RTI &gt;
Figure 215a shows examples of transverse cross-sections created by Fourier series expansions of a pressurized chamber in which the transverse cross-sectional area is reduced while the circumferential periphery size remains constant.
Figure 215b shows a variant of the pressure chamber of Figure 207a in which the pressurizing chamber is now in a fixed transverse direction designed in such a way that the area is reduced during the pump stroke while its outer periphery is kept approximately constant or reduced to some extent And has a longitudinal cross section having a cross section.
Figure 215c shows the transverse cross section G-G (dotted lines) and the longitudinal cross section H-H of Figure 215b.
FIG. 215D shows the cross section G-G (dotted lines) and the longitudinal section I-I of FIG. 215C.
Figure 215E shows other examples of cross-sectioned cross sections created by Fourier series expansions of the pressurizing chamber, where the cross-sectional area is reduced while the circumferential periphery size remains constant.
Figure 215f shows an example of an optimized convex shape of the cross section in the cross section under certain constraints.
Figure 216 shows a combination in which the piston moves in a cylinder on a tapered center.
Figure 217a shows an ergonomically optimized chamber for pumping purposes and manual operation.
Figure 217b shows the corresponding force-stroke diagram.
Figure 218a shows an example of a movable power unit suspended below a parasitic.
Figure 218b shows the details of the movable power unit.
507 Description of Drawings
BRIEF DESCRIPTION OF THE DRAWINGS The foregoing features and other aspects of the invention are set forth in the following description in conjunction with the accompanying drawings.
Figure 301 shows a first embodiment of a valve actuator in a clip-on valve connector to which a shrouder valve can be coupled.
Figure 301A shows an enlarged view of the detail of Figure 301 with channels around the piston.
FIG. 301B shows a section G-G of FIG. 310A.
Figure 302 shows a second embodiment of a valve actuator in a universal clip-on valve connector with streamed activation pins.
FIG. 302A shows an enlarged view of a detail portion of FIG.
Figure 302B shows a cross section H-H of Figure 302A.
Figure 303 shows a third embodiment of the valve actuator in the compression valve connector.
Figure 303a shows an enlarged view of the details of Figure 303;
304 shows a wall of a valve actuator and cylinder including an activation pin in a permanent assembly (e.g., from a chemical plant).
Figure 305 shows a fourth embodiment of a valve actuator in a universal valve connector.
19597 Brief description of drawing
Hereinafter, preferred embodiments of the invention will be described with reference to the drawings, wherein the invention is specifically described below with reference to the drawings and the drawings. The following is illustrated in the figures and figures, wherein the transverse cross section refers to the cross section perpendicular to the direction of movement of the piston and / or chamber, while the longitudinal cross section is along the direction of the direction of movement:
401a shows a top view of the pump of the floor pump type of FIG. 401b, wherein the combination can rotate about the line XX, YY or ZZ with respect to the floor surface, while the angle is not limited by suspension.
401b shows a rear view of the floor pump of FIG.
Figure 402a shows a top view of the pump of the floor pump type of Figure 402b, wherein the combination can move three-dimensionally with respect to the surface while the angle is the spring force of the transition between the combination and the deflection Lt; / RTI &gt;
Figure 402 (b) shows a rear view of the floor pump.
Figure 402c shows a top view of the pump of Figure 402b, wherein the handle has been moved to a position in front of its rest position.
Figure 402d shows a top view of the pump of Figure 402b, wherein the handle has been moved to a position behind its rest position.
Figure 402e shows a top view of the pump of Figure 402b, wherein the handle has been moved to its left position in front of its rest position.
FIG. 402f shows a top view of the pump of FIG. 402b, wherein the handle has been moved to its left position behind its rest position.
Fig. 402g shows a top view of the pump of Fig. 2b, wherein the handle has been moved to the right position in front of its position when it is not functioning (out of function).
Figure 402h shows a top view of the pump of Figure 402b, wherein the handle has been moved from the rear of its rest position to the right position.
403a shows a side view of a floor pump having a flexible transition between a combination and a basis.
Figure 403b is an enlarged view of the transition portion of Figure 403a.
Figure 403c shows a rear view of a floor pump with another flexible transition between the chamber and basis of the combination.
Figure 403d shows an enlarged view of the transition portion of Figure 403c.
404a shows a rear view of a floor pump with a cap that allows the piston rod to move in the cross direction of the combination.
Figure 404b shows an enlarged view of the cross-section of the cap of Figure 404a when the piston rod is pulled out of its maximum, without transverse movement.
Figure 404c shows a cross-sectional view of Figure 404b as the piston rod is pulled out of its maximum, with the piston rod being rotated to the left.
Figure 404d shows an enlarged view of the transverse cross section of the cap of Figure 404a when the piston rod is not pulled out-there is no transverse movement.
Figure 404e shows a cross-sectional view of Figure 404d when the piston rod is not pulled out, with the piston rod transversely translating to the left.
Figure 405a shows a plan view of the floor pump type of Figure 405b wherein the angle between the centerlines of the handle portions opposite the centerline of the combination is less than 180 °.
Figure 405b is a side view of the handle of the floor pump of Figure 405a.
Figure 406a shows a top view of the floor pump type of Figure 406b, wherein the angle between the centerlines of the handle portions opposite the centerline of the combination is greater than 180 °.
Figure 406b is a side view of the handle of the floor pump of Figure 406a.

19627 Description of the Preferred Embodiment

In the following, preferred embodiments of the invention will be described with reference to the drawings.

1-3 handle the limitation of the stretching of the wall of the piston. This includes the limitation of stretching along the length direction when the piston is exposed to pressure in the chamber and allows expansion in the transverse direction when moving from the second longitudinal position to the first longitudinal position.

Stretching along the length of the wall of the container-type piston may be limited by several methods. Such limitations may be achieved, for example, by reinforcement of the wall of the container by use of textile and / or fiber reinforcement. Such limitations may also be achieved by placing an expansion body within the chamber of the container which is connected to the wall of the container while the expansion is restricted. Other methods may be used, for example, management of the chamber between two walls of the container, pressure management of the space above the container, and the like.

The expansion behavior of the walls of the container may depend on the type of stretch restriction utilized. Also, during expansion, holding a moving piston on the piston rod may be induced by a mechanical stop. The placement of such stops may depend on the use of a piston-chamber combination. This may also be the case for guidance of the container on the piston rod during expansion and / or during exposure to external forces.

Any kind of fluid could be used - a combination of compressible and non-compressible media, a compressible medium alone or an uncompressible medium alone.

A change in the size of the container may be made from substantially the smallest cross-sectional area, where it has a production size and is expanded in the largest cross-sectional area, and the first enclosed space of the chamber in the container, It is possible that communication with In order to maintain the pressure in the chamber, the first enclosed space may also be pressed during changes in the volume of the chamber of the container. Pressure management for at least the first enclosed space may be required.

Figure 1a shows a chamber 186 having a concave wall 185 and a container 208 (= first longitudinal position within the chamber 186) at the beginning of the stroke and a container 208 ' (E.g., a second longitudinal position within the expandable piston 186). The center axis of the chamber 186 is '184'. The container 208 'shows its production size and has a textile reinforcement 189 within the skin 188 of the wall 187. During the stroke, the container wall 187 stops moving and / or other stationary arrangements that can utilize the mechanical stop 196 outside the textile reinforcement 189 and / or the container 208 during the stroke Until it is swollen. As a result, the container expands. Depending on the pressure in the chamber 186, due to the pressure in the chamber 186, longitudinal stretching of the walls of the container may still occur. However, the main function of the reinforcement is to limit this longitudinal stretch of the wall 187 of the container 208. During the stroke, the pressure inside the container 208, 208 'may be kept constant. This pressure depends on the variation of the volume of the container 208, 208 ' and therefore on the change in the circumferential length of the cross section of the chamber 186 during stroke. Also, pressure variations during the stroke may be possible. Also, depending on the pressure in the chamber 186, or not, the pressure may be varied during the stroke.

FIG. 1B shows a first embodiment of a piston 208 that is expanded at the beginning of the stroke. A wall 187 of the container may be constructed by a skin 188 of flexible material and the skin may be a rubber type or the like having a textile reinforcement 189 that allows for expansion. The direction (= braid angle) of the textile reinforcement with respect to the central axis 184 is different from 55 ° 44 '. The change in size of the piston during the stroke does not necessarily result in the same shape as shown. Due to the expansion, the thickness of the walls of the container may be less than the wall thickness of the container as produced when it is placed at the end of the stroke (= second longitudinal position). There may be an impermeable layer 190 inside the wall 187. Such an impermeable layer is tightly compressed within the cap 191 at the upper end of the container 208, 208 'and the cap 192 at the lower end. The details of the caps are not shown and all kinds of assembly methods can be used - these methods will be able to adapt themselves to the varying thickness of the walls of the container. Both caps 191, 192 can translate / rotate above the piston rod 195. Such movements may be accomplished by a variety of methods, such as, for example, different types of bearings not shown. The cap 191 in the upper end of the container may be moved upward and downward. The stop 196 on the piston rod 195 on the outer side of the container 208 restricts upward movement of the container. The cap 192 in the lower end will only be able to move downward because the stop 197 will prevent upward movement-this embodiment can be used in a piston chamber device having a pressure in the chamber 186 below the piston It can be thought that it can be done. Other arrangements of stops may be possible, for example, in other pump types such as dual task pumps, vacuum pumps, etc., and only depend on the design specifications. Other arrangements may be made to enable and / or limit the relative movement of the piston relative to the piston rod. The tuning of the sealing force may include a combination of the non-compressible fluid 205 and the compressible fluid 206. The wall 185a of the chamber 186 is parallel to the central axis 184. Which is disposed close to the first longitudinal positions at the end of the stroke. The container 209 can communicate with the second chamber 210 including the spring force operated piston 126 inside the piston rod 195 while the container 209 is in communication with the second chamber 210, will be. The fluid (s) will be able to flow freely through the hole 201 and through the wall 207 of the piston rod. While the second chamber can communicate with the third chamber (see FIG. 12), the pressure inside the container may also depend on the pressure in the chamber 186. The container may be inflated through the piston rod 195 and / or by communication with the chamber 186. O-rings or similarities (202, 203) in the cap within the cap in the upper end and the cap in the lower end respectively seal the caps (191, 192) against the piston rod. The cap 204 shown as an assembly screwed at the end of the piston rod 195 tightens the piston rod. Depending on the desired movement of the walls of the container, comparable stops may be located at any point on the piston rod. The contact area between the wall of the container and the wall of the chamber is '198'.

Fig. 1c shows the piston of Fig. 1b at the end of the pump stroke, where the piston has a production size. The cap 191 in the upper end portion is moved from the stop portion 196 over a distance a '. The spring force operated valve piston 126 is moved over a distance b '. The lower end cap 192 is shown adjacent to the stop 196 and the lower end cap 192 is pressed against the stop 196 when pressure is present in the chamber 186. Compressible fluid 206 'and non-compressible fluid 205'. Contact area 198 'between the container 208' and the wall of the chamber at the second longitudinal position.

Wall 185b of chamber 186 parallel to central axis 184. The wall is disposed close to the second longitudinal positions at the end of stroke.

Figure 2a shows the longitudinal direction of an expandable piston including a chamber 186 having a concave wall 185 and a container 217 'at a first longitudinal position of the chamber and a container 217' at a second longitudinal position FIG. The container 217 'shows its production size and has a fiber reinforcement 219 in the skin 216 of the wall 218 according to the lattice effect. During the stroke, the walls 218 of the container (s) 218 may be removed from the container until the stop arrangement, which may be a fiber reinforcement 219, and / or mechanical stops 214 and / Expands. The main function of the fiber reinforcement is to limit the longitudinal stretching of the wall 218 of the container 217. During the stroke, the pressure inside the containers 217 and 217 'may be kept constant. This pressure depends on the change in the volume of the container 217, 217 'and thus on the change in the circumferential length of the cross section of the chamber 186 during the stroke. Also, depending on the pressure in the chamber 186, or not, the pressure may be varied during the stroke. A contact area (211) between the wall of the chamber at the first longitudinal position and the container (217).

Figure 2B shows a second embodiment of the piston 217 expanded at the beginning of the stroke. A wall 218 of the container is constructed by a skin 216 of flexible material and the skin is provided with a fiber reinforcement 219 which permits expansion of the container wall 218, Water, and accordingly the direction of the fibers (= braid angle) with respect to the central axis 184 may be different from 55 ° 44 '. Due to the expansion, the wall thickness of the container may be less than the wall thickness of the container as produced when the wall is positioned at the end of the stroke (= the second longitudinal position), but it is not necessarily significantly different. There may be an impermeable layer 190 inside the wall 187. Such an impermeable layer is tightly compressed within the cap 191 at the upper end of the container 217, 217 'and the cap 192 at the lower end. The details of the caps are not shown and all kinds of assembly methods can be used - these methods will be able to adapt themselves to the varying thickness of the walls of the container. Both caps 191, 192 can translate / rotate above the piston rod 195. Such movements may be accomplished by a variety of methods, such as, for example, different types of bearings not shown. The cap 191 in the top portion will be able to be moved up and down until the stop 214 restrains movement. The cap 192 in the lower end will only be able to move down because it prevents the upward movement of the stop 197 - this embodiment can be used in a piston chamber device having a pressure in the chamber 186 It can be thought. Other arrangements of stops may be possible, for example, in other pump types such as dual task pumps, vacuum pumps, etc., and only depend on the design resources. Other arrangements may be made to enable and / or limit the relative movement of the piston relative to the piston rod. The tuning of the sealing force may include a combination of the uncompressible fluid 205 and the compressible fluid 206 inside the container (both of which are also possible alone), while the chambers 215 Will be able to communicate with the second chamber 210 comprising the spring force actuating piston 126 within the piston rod 195. The fluid (s) will be able to flow freely through the hole 201 and through the wall 207 of the piston rod. While the second chamber can communicate with the third chamber (see FIG. 12), the pressure inside the container may also depend on the pressure in the chamber 186. The container may be inflated through the piston rod 195 and / or by communication with the chamber 186. O-rings or similarities (202, 203) in the cap within the cap in the upper end and the cap in the lower end respectively seal the caps (191, 192) against the piston rod. A cap 204, shown as a screwed assembly at the end of the piston rod 195, tightens the piston rod. The wall 185a of the chamber 186 is parallel to the central axis 184. [ Which is disposed close to the first longitudinal positions at the end of the stroke.

Figure 2c shows the piston of Figure 2b at the end of the pump stroke with a production size. The cap 191 is moved over the distance c 'from the stop 214. The spring force operated valve piston 126 has moved over a distance d '. The lower end cap 192 is shown adjacent to the stop 197 and the cap 192 is pressed against the stop 197 when there is pressure in the chamber 186. Compressible fluid 206 'and non-compressible fluid 205'. The contact area 211 'of the container 217' and the wall of the chamber 186 in the second longitudinal position.

The wall 185b of the chamber 186 is parallel to the central axis 184. Which is disposed close to the second longitudinal positions at the end of the stroke.

Figures 3a, 3b and 3c illustrate an inflatable piston comprising a container 228 at the beginning of the stroke and a container 228 'at the end. The production size is the production size of the piston 228 'in the second longitudinal position within the chamber 186. 7a, 7b, and 7c, except that the reinforcement portion includes any type of reinforcement means that can be bendable and can be placed in a pattern of reinforcing "columns" that do not intersect with each other. It can be the same. This pattern may be parallel to the central axis 184 of the chamber 186 or a portion of the stiffening means may be in a plane through the central axis 184. [

Figure 3B shows a wall 218 having skins 222 and 224. Reinforced portion 223. A contact area 225 between the container 228 and the wall of the chamber in a first longitudinal position. Impermeable layer (226).

Figure 3c shows a contact area 225 'between the container 228' and the wall of the chamber in a second longitudinal position.

Fig. 3d shows a top view of the pistons 228 and 228 ', each having respective stiffening means 227 and 227'.

Figure 3e shows a top view of the pistons 228 and 228 ', respectively, having respective stiffening means 229 and 229'.

Figure 4 shows the position at which the contact surface 225 'is present between the piston 228 " and the wall 185 of the chamber 186, while there is no pressure differential in the chamber between the opposite sides of the piston. Moving inflatable piston 228 'within a chamber 186 having a wall 185a parallel to the central axis 184 of the chamber 186. In addition to the first position, (Center) 1001 of the resiliently deformable wall of the piston on the central axis 184. The projections 1000 of the intermediate point (center)

Figure 5a shows the piston of Figure 4 in a non-moving manner within a chamber 186 having an instantaneously conical wall 185 where the piston begins to expand and the movable cap 191 move toward the non-movable cap 192. The contact surface 225 "has increased and is now positioned below the respective centers 1002 and 1003 of the resiliently deformable wall of the piston-the protrusions each have a central axis 1004 The direction of movement 1006 of the movable cap 191. The force 1007 from the wall 187 of the piston to the wall 185 of the chamber 186, Distance (g ').

Figure 5b illustrates the piston of Figure 5a wherein the piston is momentarily non-mobile and thus expands and thus contacts the region 185 of the piston 187 with the wall 185 of the chamber 186 Quot;) is increased at the second longitudinal positions of the contact surface 225 "'and the movable cap 191 is currently non-mobile. The contact surface 225 "'is about the point where the midpoint (center) is the point of the elastically deformable wall of the container. Centers 1008 (spheres) of the elastically deformable wall of the piston and 1011 The piston walls 187 on the wall 185 of the chamber are in the form of protrusions 1010 and 1011 on the central axis, The direction 1012 of movement of the force 1012. The movement 1014 of the movable cap 191.

Figure 5c illustrates the piston of Figure 5b which is momentarily non-mobile and thus expands so that the contact area 225 "" of the piston wall 187 with the wall 185 of the chamber 186, ) Is reduced at the second longitudinal positions of the contact area, while the area of contact of the piston wall with the wall of the chamber is increased at the first longitudinal positions of the contact area - the movable cap non- to be. The centers of the elastically deformable walls of the piston 1015 (spheres) and 1016 (new) - the protrusions are on the protrusions 1017 (old) and 1018 . Distance (g '). The direction of movement 1019 of the reaction force 1020 of the wall of the chamber on the wall 187 of the piston. The direction of movement 1021 of the wall 187 of the piston.

Figure 5d shows the piston of Figure 5c where the non-movable cap 192 instantly begins to move from the second longitudinal position to the first longitudinal position, thereby moving the piston in the same direction . The contact area 225 "'is considerably smaller than the contact area 225" " of FIG. 5C. Distance (h '). Projections 1022 of the center 1023 of the resiliently deformable wall of the piston on the central axis 184, respectively. The direction of movement 1024 of the movable cap 191 and the direction of movement 1025 of the non-movable cap 192, and thus the direction of movement of the entire piston. Leakage occurring at that time (1026).

5D shows the piston of Fig. 5D where the movement of the piston is reduced due to the increased contact area 225 "". The central axis 184 of the elastically deformable wall center 1028 of the piston The moving direction 1029 of the movable cap 191. The moving directions 1030 and 1031 of the wall of the piston.

Figure 6a shows a coupling and / or seal (not shown) in a cone-shaped chamber 899, including a reinforced (not shown) wall 901, embedded in a non- Lt; RTI ID = 0.0 &gt; (900). &Lt; / RTI &gt; The cap 904 is hollow and is slidably movable on the piston rod 902, including the enclosed space, and in communication with the space within the piston 898. There is a fluid or a mixture of fluids in the piston. The chamber may be closed at both sides of the piston into spaces 906 and 907 and may contain a fluid or a mixture of fluids at one or both sides of the piston 898. [ A contact area 905 between the wall 901 of the piston 898 and the wall 897 of the chamber 899. The presence of fluid at both sides of the piston will allow the piston to move in a different manner than desired.

6B is a side view of the piston 898 shown in Fig. 6A moving conjointly and / or sealingly (900) in a cone-shaped chamber 896 with spaces 908 and 909 on each side of the piston 898 The piston 898 is shown. A tube 911 is positioned within the wall 895 of the conically shaped chamber 896 at the first longitudinal positions which allows communication between the atmosphere 910 of the peripheries and the space 908, 912 are assembled in the wall 895 of the cone-shaped chamber 896, which allows communication between the generally 910 of the peripheries and the space 909. A contact area 905 between the wall 901 of the piston 898 and the wall 897 of the chamber 896. The atmosphere of the periphery (910). A contact area 905 between the wall 901 of the piston 898 and the wall 897 of the chamber 896.

6C is a cross-sectional view of the piston 898 shown in FIG. 6A moving conjointly and / or sealingly (900) in a cone-shaped chamber 894 having spaces 908 and 909 on each side of the piston 898 The piston 898 is shown. A tube 913 is placed in the wall 893 of the conically shaped chamber 894 at the first longitudinal positions and is assembled within the wall 893 of the conically-formed chamber 896, Allowing communication between the interior of the tube 915 and the space 908 in communication with the tube 914 in communication with the space 909 of the shaped chamber 894. A contact area 905 between the wall 901 of the piston 898 and the wall 893 of the chamber 896.

Figure 6d shows a piston 892 that moves in a conical manner within a conical-shaped chamber 899 with spaces 906 and 907 at each side of the piston 892. [ The spaces 906 and 907 communicate with each other through a tube 918, assembled within the caps 891 and 890, respectively. A contact area 905 between the wall 901 of the piston 898 and the wall 897 of the chamber 899.

6E shows a piston 898 that is moveably engageable within a cone-shaped chamber 899. The chamber may be closed at both sides of the piston into spaces 906 and 907 and may contain a fluid or a mixture of fluids at one or both sides of the piston 898. [ There is no contact area between the inner wall 922 of the cone-shaped chamber 899 and the outer wall 923 of the piston 924 and instead a gap 920 is formed between the walls 922 and 923, To allow fluid 921 to flow in a direction opposite to the direction of movement 900 of the piston 898.

Figure 6f shows a cross sectional view of a portion of the duct 926 that is formed by three ducts uniformly spread over the contact area 927 of the wall 928 of the actuator piston 925 and the wall 922 of the chamber 899, On the basis of the piston 924 shown in Fig. 6E, having a piston 926. The actuator piston 925 is shown in Fig. The ducts 926 allow fluid communication between the two spaces 906 and 907 of the chamber 899. The portion 929 of the contact area 927 where sealing contact with the wall 922 of the chamber 899 along the periphery is generated is smaller than the case where the ducts 926 are not present, 925 may still be acceptable. The length of the duct 926 along the longitudinal direction is greater than the longitudinal length of the contact region 927 in order to obtain communication between the spaces 906 and 907 of the chamber 899 at all longitudinal positions. It is longer. Piston rod 929. Movable cap 930;

Figure 6g shows a view of the actuator piston 925 from the transverse cross-section and first longitudinal position of the piston rod 929 of Figure 6f. The chamber wall 922. Movable cap 930; The duct 926 generally equally upwardly divides the outer circumference of the actuator piston 925 in the area of contact 927 with the wall 922 of the chamber 899.

Figure 7a shows the piston of Figure 1c at the end of the pump stroke. The walls of the chamber are parallel to the central axis 184 and this explains why the container is non-movable even when it is pressurized.

Figure 7b shows the piston of Figure 7a in the portion of the chamber where the walls are not parallel to the central axis and have a positive angle. The piston will move toward the first position because the intermediate point of the flexible wall is on the contact surface with the wall.

Figure 7d is a three dimensional view and illustrates a reinforcing matrix of textile material that permits elastic expansion and contraction of the walls of the containers 208, 208 'when sealingly moving within the chamber 186 .

The textile material may be elastic and is disposed on top of each other in independent layers. In addition, the layers may be woven together and positioned. The angle between the two layers may be different from 53 ° 44 '. When the material type and thickness are the same in all layers and the number of layers is even while the stitch sizes for each direction are the same and the expansion and contraction of the walls of the container may be the same in the X, There will be. As the stitches ss and tt expand, the matrix will begin to grow along each direction, respectively, while their contraction will begin to decrease. As the material of the threads is elastic, other devices such as mechanical stops may be needed to stop the expansion. This could be the mechanical stop shown on the walls of the chamber and / or on the piston rod, as shown in Figure 7B.

Fig. 7e is a three-dimensional view, and shows the reinforced matrix of the expanded Fig. 7d. The stitches ss 'and tt' are larger than the stitches ss and tt. As a result of the shrinkage, the matrix shown in Fig. 7D may result.

Fig. 7f is a three-dimensional view and can be fabricated with inelastic threads (but may be elastically bendable) and can be fabricated from reinforcing textile materials that are positioned on separate layers above one another or knitted together Lt; / RTI &gt; When placed in the second longitudinal position of the chamber, expansion is possible due to the extra length of each loop 700 available, which is also when the container is at production size - also pressurized. Stitches ss "and tt" along the respective directions. As the wall of the container expands, the inelastic material (but elastically bendable) will be able to limit the maximum expansion of the wall 187 of the container 217. It may be necessary to stop the movement of the container 217 on the piston rod 195 by, for example, the stop 196 so that the seal can be maintained. If such stop 196 is missing, it may be necessary to create a valve.

Figure 7g is a three-dimensional view and shows the reinforced matrix of Figure 7f, which has been expanded. The stitches ss "'and tt' 'are larger than the stitches ss" and tt ". The result of the contraction may result in the matrix shown in Fig.

Figure 8 illustrates an alternative embodiment of the invention in which the piston is moved in an elastically deformable container 372 in which the tapered wall 373 shown in the center around the central axis 370 and the chamber 375 in the cylinder wall 374, Lt; RTI ID = 0.0 &gt; 372 &lt; / RTI &gt; The piston is suspended within at least one piston rod (371). Containers 372 and 372 'are shown at a second longitudinal position and at a first longitudinal position 372 of the chamber 372'.

All of the solutions disclosed herein may also be combined with piston types, wherein chambers having cross sections of constant circumferential peripheral sizes may be a solution to the jamming problem.

Figure 9A shows a longitudinal section of a chamber having an inflatable piston and a convex / concave wall 185 that includes a container 258 at the beginning of the stroke and a container 238 'at the end. The container 258 'represents its production size.

Figure 9b shows a side view of the skins 252 and 254 reinforced by a plurality of at least elastically deformable support members 254 rotationally fastened to a common member 255 connected to the skins 252 of the pistons 258 and 258 ' And a wall 251. The piston 258, These members are in a tensile state, and depending on the hardness of the material, the members have a certain maximum elongation length. This limited length limits the extension of the skin 252 of the piston. The common member 225 will be able to slide with the sliding means 256 on the piston rod 195. And the rest is a configuration comparable to the configuration of the pistons 208 and 208 '. Contact area (253).

Figure 9c shows a longitudinal cross section of the piston 258 '. Contact area 253 '.

Figure 9d shows a longitudinal section of the piston 258 " with a common area 253 ". Center 1020 of the resiliently deformable wall 251 of the piston. The protrusion of the center point 1020 on the central axis 1022.

Figures 10a-f (included) illustrate the pressure arrangement of a combination of expandable actuator pistons, operating in a chamber, wherein the chamber has a cross-section of different cross-sectional areas at different first and second longitudinal positions, Sectional areas and circumferential lengths that are at least substantially continuously different at mid-longitudinal positions between said first and second longitudinal positions, said cross-sectional and circumferential lengths at said second longitudinal position being substantially equal 1 is less than the cross-sectional and circumferential length at the longitudinal position and the magnitude of the volume of the enclosed space is constant when the actuator piston operates from the second longitudinal position to the first longitudinal position. This could be done with two technologies (CT and ESVT).

10g-1 (inclusive) shows the pressure arrangement of a combination of expandable actuator pistons, operating in a chamber, the chamber having a cross-section of different cross-sectional areas at different first and second longitudinal positions and a different circumferential length Sectional areas and circumferential lengths that are at least substantially continuously different at mid-longitudinal positions between said first and second longitudinal positions, said cross-sectional and circumferential lengths at said second longitudinal position being substantially equal 1 &lt; / RTI &gt; in the longitudinal position and the size of the enclosed space is reduced when the actuator piston operates from the second longitudinal position to the first longitudinal position. This is done to reduce the volume of the pressurized medium, thereby reducing the energy available for re-pressurization of the medium. This can be done in embodiments that preferably use ESV technology because the change in the size of the enclosed space volume is much easier than in embodiments using Comsumption Technology.

10A shows a piston-chamber combination with a chamber 186 having a center line 184 and a wall 185 of a chamber 186 wherein the piston 217'pressed in an oval shape - (207, 653, 19660 and 19680) - moves from the second longitudinal position 2000 to the first longitudinal position 2001 (2003). The first longitudinal position 2001 has a piston 217 'expanded into the piston 217 having a spherical shape while having a fixed volume of the enclosed space 210. This means that the pressure in the piston 217 is gradual during movement 2003 and has its minimum value in the first longitudinal position 2001. The shape of the piston 217 may also be elliptical (not shown) in the first longitudinal position - as described and illustrated in section 19660 herein, Will increase. The position 2004 of the valve 126 is not changed during this operation, so that the volume of the enclosed space 210 is maintained unchanged. The arrow 2005 indicates that the next stage of operation is shown in Fig. 10b or 10c, and that shown in Fig. 10c is shown by the arrow 2011.

Position 2025 shows piston 217 'in a second longitudinal position, wherein wall 2030 of chamber 186 is parallel to center axis 184. At the first longitudinal position, the piston 217 becomes the position 2026, wherein the wall 2031 of the chamber 186 is parallel to the central axis 184. Shape 2027 shows when the piston is in its first longitudinal position and the piston begins to be (retarded) depressurized. The shape and size 2028 is when the piston 217 "is about half of the return stroke, where the wall 185 of the chamber 186 becomes free of membrane due to the delayed depressurization. The same shape and size 2008 of the piston 217'is due to its engagement with the wall 185 of the chamber 186 (and not being free from the wall), so that the piston 217 " (Distance y) relative to the second longitudinal position as compared to when moving to the second longitudinal position.

The size of the enclosed space under the valve 126 is determined by the length of the channel to the lower end of the piston rod - this length is 'a' at the second longitudinal position and 'b' at the first longitudinal position , Where a = b.

Figure 10B illustrates that valve 126 is retracted further 2006 from its position 2004 to position 2007 (2006). Enclosed space 210 '. As a result, the volume of the enclosed space 210 'is greatly reduced, so that the pressure inside the piston 217 "becomes substantially equal to the pressure at which the piston was produced (e.g., atmospheric pressure) The size and shape are substantially equal to the size and shape when the piston is in the second longitudinal position 200 and this returns from the first longitudinal position 2001 to the second longitudinal position 2000 , The piston 217 "may &lt; / RTI &gt; be unjoined and / or coupled, but not the wall 185 of the chamber 186. The wall of the piston (2024).

When the piston 217 "moves from the first longitudinal position 2001 to the second longitudinal position 2000, a relatively slow internal pressure drop may be obtained so that the piston 217B" Will still have an elliptical shape that is larger than the shape of the piston 217'in the second longitudinal position 2000 so that during the movement 2008 the piston 217B "is engaged with the wall 185 The same size of the piston 217B "is defined such that the piston is moved from the second longitudinal position 2000 (sealingly and / or conjointly) to the first longitudinal position &lt; RTI ID = Lt; RTI ID = 0.0 &gt; (2001) &lt; / RTI &gt; The pressure drop may also be obtained already in the first longitudinal position 2001.

When the piston 217 ", 217B "is returned to the second longitudinal position 2000, the position of the valve 126 in the enclosed space 210 'is changed from 2007 to 2004 and indicated by arrow 2009 - so that the enclosed space 210 'again has the original volume of FIG. 10A, so that the piston 217' again has its original pressure. Arrow 2010 indicates that the next stage of operation is shown in Fig. 10a.

Figure 10c shows an alternative solution for changing the internal pressure of the piston 217 and will be considered in conjunction with Figure 10a in which the valve 126 is omitted and instead an inlet / May be present-see, for example, Figures 210a-f (inclusive) and Figures 211a-f (inclusive) of section 653 of the present application. The pressurized piston 217 'moves from the second longitudinal position 2000 to the first longitudinal position 2001 (2003), as shown in FIG. 10A. No addition or removal of fluid to the enclosed space 210 occurs. Arrow 2011 indicates that the next stage of operation is shown in Fig. 10C. The reduced pressure in the piston 217 "is obtained by removing the required amount of fluid from the enclosed space 210: arrow 2020. As the piston 217" moves from the first longitudinal position 2001 (arrow 2021) (Arrow 2022) with the piston 217 "- the arrow 2023 is moved to the second longitudinal position 2000 when the next fluid phase is added to the enclosed space 210, ) Is shown in Figure 10a, resulting in a piston 217 "'. The wall of the piston (2024).

It can be emphasized that the combination of all of the above techniques can be an additional solution for pressure management of the piston. Additionally, under the condition that during the return from the first longitudinal position 2001 to the second longitudinal position 2000, only the wall 2024 of the piston engages or does not engage with the wall 185 of the chamber 186, The pressure drop from the piston 217 or 208 to the piston 217 "or 208", respectively, may be gradual - e.g., computerized.

The wall 185 of the chamber 186 of Figures 10A-1 at the second and first longitudinal positions may not be parallel to the central axis. There are no channels as shown in Figures 4, 5a-e (inclusive).

Figures 10d-f illustrate a process similar to that shown in Figures 10a-c, with a spherical shaped piston 208 now.

10g-i illustrate a process similar to the process shown in Figs. 10a-c, with the difference that when the piston 217 'moves from the second longitudinal position 2000 to the first longitudinal position 2001, , Where the valve 126 is not substantially removed from the lower end of the piston, as shown in Figure 10A. The length of the piston rod below the piston 216, which gives the magnitude of the enclosed space volume, is 'e' while this length between the second longitudinal position and the first longitudinal position is reduced to 'f' At the first longitudinal position the length is further reduced to 'g', where e> f> g.

10J-1 shows a process comparable to the process shown in Figs. 10d-f, wherein the pressure is maintained as described in Fig. 10g, but now has a spherically shaped piston 208. Fig. The length of the piston rod below the piston 216, which gives the magnitude of the enclosed space volume, is 'h' while this length between the second longitudinal position and the first longitudinal position is reduced to 'i' At the first longitudinal position the length is further reduced to 'j', where h> i> j.

11f, 11g (crankshaft) and Figs. 13f, 13g, 14a-c are shown in Figs. 10a, 10b or 10d, 10e. is used in a motor according to the present invention shown in h (inclusive) (rotary).

The process shown as C (onsumption) T (technology) shown in Figures 10a, 10c or 10d, 10f and 210a-f (inclusive) and 211a-f (inclusive) Crankshaft) and Figs. 12a-c (inclusive), 13a-d (inclusive).

Figure 10m shows the motor and B-B section of Figure 12c (and the B-B section can be partially seen in Figure 12a), wherein the piston of the actuator piston-chamber combination is moved, while the chamber is not moved. The motors include four sub-chambers 961, 962, 963, and 964, extending axially about the same central axis 965, with axles 966 through the center 967 of the chamber 960, And a chamber 960, respectively. One piston 968 is disposed within each of the sub-chambers 961, 962, 963, and 964, wherein two major positions, i.e., the sub-chamber 964 having the largest diameter, Chamber 961 ' when in the first rotational position, i.e., at position 968 &apos; in the second rotational position of sub-chamber 961, which is contiguous with position 968 &apos; Chamber 964 is located closest to the second rotational position of lower-chamber 961 and has the smallest diameter in the second rotational position. The actuator piston 968, Is shown clockwise about the axle 966 and shows four holes 970 for assembling the chamber 960 on the axle 966.

Figure 10n shows a cross section B-B of Figures 13a and 13b and the motor is of a type in which the chamber of the actuator piston-chamber combination moves and the piston does not move. The motor comprises a chamber 860 and the chamber comprises a respective, four sub-chambers 861, 862, 863 and 864, the sub-chambers being connected to one another and around the same central axis 865 Which has an axle 866 through the center 867 of the chamber 860. Inside each of the lower-chambers 861, 862, 863, and 864, there are disposed in each of the lower-rotation chambers 861, 862, 863, and 864 at different angles? Five pistons 868, 869, 870, 871, and 872 are disposed, respectively. Each piston includes a piston rod 873, 874, 875, 876 and 877, respectively. The pistons 868, 869, 870, 871 and 872 are of the "spherical-spherical" type and are shown as having both different diameters. The chamber 860 rotates clockwise about the axle 866 and the lower chambers 861, 862, 863 and 864 rotate in the clockwise direction to a second rotational position and a first rotational position Four holes 878 for assembly of the chamber 860 on the axle 866 are shown.

The motors according to FIGS. 10g and 10h may include a chamber 860, and at least a portion of the chamber may be parallel to the central axis (not shown) of the chamber.

A circular chamber comprising the same sub-chambers may comprise an actuator piston inside each of the lower-chambers, and all actuator pistons are located at the same circular point in each lower-chamber.

Calibrated 19615 - associated with the pressure management system for Figures 11f, 13f and 13e

Whether a change in direction can cause a loss of pressure-which may be caused by "consumption" of the fluid-whether a repressurization system is needed may be determined by a bi- directional actuator (e.g., And 1057), and the fluid will be able to be released into the atmosphere during a direction change, or may also be caused by a pressure drop - see Figure 13e. The repressurization system may be similar to that shown in the preceding figures, e.g., Figs. 11A, 11B and 12A.

A system could be developed that can "consume" the fluid without "consuming" the fluid. In Figures 11f and 13f, this is considered to be already proposed, so that only a certain volume of pressure storage container may be needed. The pressure is preferably low (e. G., 10-15 bar) and optionally high (e. G., 300 bar).

Such a system may include a typical cylinder, in which a bi-directional piston is disposed. A cylinder inlet and an outlet valve on each side of the piston so that the inlet valve on one side communicates with the outlet valve on the other side of the piston. Thus, the total accumulated volume on both sides of the piston can be kept constant - which can lead to the fact that the piston can be moved from one side of the cylinder to the other without fluid consumption. Pressure is also consumed. This may be achieved, for example, by the presence of only electricity present to control the valves, and which can be connected to the main axle by a sustainable power supply, for example, solar photovoltaic cells, such as a bolt and / Lt; / RTI &gt; can be derived very easily from the accumulator loaded by the &lt; RTI ID = 0.0 &gt; This reduces the additional energy still required for such motors. It is conceivable that the pressure storage vessel is loaded in the production of the motor.

Instead of a bi-directional actuator, an electric stepping motor may be used and controlled by a computer. Such a motor will be able to react sufficiently precisely and quickly to the control impulses from the computer.

Also, the system 4 shown in FIG. 13F, which cites 1093 and 1094, could be used here.

11f, the description of the preferred embodiments

Holes in the piston rod 805 in the container piston 810 are not shown in the container piston 810 -but they are already shown in Figures 2b, 2c, 201 and will be present in Figure 11f.

The addition to the description of the preferred embodiments with respect to Figure 13f

Holes in the piston rod 805 in the container piston 810 are not shown in the container piston 810 - but these will already be shown in Figures 1b, 1c, 201 and in Figure 13f.

11A, 11B, and 11C.

The fluid in the actuator piston is depressurized and then pressurized by the system and the space in the piston is sequentially connected and disconnected with the re-pressurization pump and pressure reservoir (Figures 11a, 11b, 11d), respectively, When connected to the main axle by the crankshaft, the following references are made.

When the depressurized-actuator piston moves from the first longitudinal position to the second longitudinal position, when the pressure vessel (e.g., Fig. 11b - reference numeral 314) and the actuator piston so that when the piston is in its second, farthest position, the piston is immediately urged. At that moment, the pressure storage vessel through the second sealed space of the crankshaft and the enclosed space of the piston rod and the piston rod in the container continuously communicating between the space inside the container and the enclosed space There is an open connection (short) between the holes, through the two holes, i.e., the holes in the crankshaft and the holes in the connecting rod.

This means that, during a stroke from the second longitudinal position to the first longitudinal position, the enclosed space of the piston has a temporarily constant volume, which, when moved, Means that the internal pressure in the container is continuously reduced due to the volume, from elliptical-spherical / spherical to spherical with large diameter / small spherical to elliptical with large circumference.

And, when reaching the furthest first longitudinal position, the internal pressure of the container may be reduced, but not at the atmospheric pressure level. The third enclosed space in the crankshaft through the two holes having the corresponding central axles at that time, that is, one in the connecting rod and the other in the crankshaft, The communication between the spaces in the container and the spaces between the space and the enclosed space of the container in the piston rod and the connecting rod may occur when returning to the second longitudinal position.

The pump communicates with the third enclosed space and sucks fluid from the container at that moment, thereby depressurizing the container.

The second enclosed space may be constantly pressurized by a constant open communication with the pressure storage vessel. Also, such connection may be controlled by a valve.

11A, 11B, &lt; RTI ID = 0.0 &gt; 11C. &Lt; / RTI &gt;

Holes in the piston rod 805 in the container piston 810 are not shown in the container piston 810 -but they are already shown in Figs. 2b and 2c, reference numeral 201, and Figs. 11a, 11b and 11c .

12A, 12B, 12C, 13A, and 13B

In the case of a circular chamber, which is a chamber with a circular central axis of rotation, with similar pressurization systems as previously mentioned with respect to crankshaft solutions (Figs. 11A, 11B and 11D), similar solutions are used in the circular chambers It may be effective, but it may be a slightly adapted way.

In the case of the moving piston and the non-moving chamber (Figs. 12A, 12B, 12C), the spherical piston may include an enclosed space communicating with the container interior space through the hole in the piston rod, And an enclosed space in communication with a second enclosed space that may be disposed within the axle. What was mentioned just before will be able to communicate with the two-way valve in the housing, which can be built around the main axle. The separator valve may be a T-valve, and the shared portion communicates with the second enclosed space. One of the non-shared portions may communicate with a pressure reservoir (e. G., Reference numeral 814) (high pressure) and the other (low pressure) You will be able to communicate. In such a manner of control, a control scheme in which the separator valve is opened and closed can be done by a computer, which compares the opening of the enclosed space and the opening of the second enclosed space in the main axle, Lt; / RTI &gt; This could also be done by a camshaft in communication with the main axle. Since there are four single chambers in Figures 12A and 12B, there must be four outlets / inlets for the second enclosed spaces present in the main axle, and also four inlets / outlets for the T- Or 4x T-valves may be present. A pump (e. G., 818, 826) may be added between the T-valve (low pressure end) and the pressure reservoir (e. G., Reference numeral 814, All of which may cause this solution to be non-optimized, for example, that transitions from and into the second enclosed space in the main axle may cause leaks.

In the case of the piston being non-movable and the chamber being mobile (FIGS. 13A and 13B), all of the lower chambers are successively disposed and communicate with each other, while five pistons may be present in the lower chamber, all having the same central circular axis There will be. Each piston communicates with the T-valve in the manner described above in the case where the piston is moving and the chamber is non-moving. Also, the pressurization system can be similar - the only difference is that there are five T-valves that can be opened / closed at different times, as each piston can be different within the same lower chambers .

Centrifugal pumps may be used instead of piston pumps (FIG. B). In a conical chamber, the efficiency of the centrifugal pumps may be lower than the efficiency of the piston pumps.

12a-c, 13a-f, the description of the preferred embodiments

The holes in the piston rod 805 in the container piston 810 are not shown in the container piston 810 -but they are already shown in Figures 1b, 1c, 201 and Figures 12a-c, 13a-f. &Lt; / RTI &gt;

The addition to the description of the preferred embodiment with respect to Figure 12c.

The outlet of the return path from the pump 1074 to the pump 1151 is connected to the storage pressure vessel 1075 by the channel 1152. [ The pump 1151 may be connected to an external, sustainable energy source such as (not shown) and / or solar power (not shown) to the main axle 966.

Figures 12a-c (inclusive), 13a-f (inclusive) Addition to the description of the preferred embodiment.

The holes in the piston rod 805 in the container piston 810 are not shown in the container piston 810 -but they are already shown in Figures 1b, 1c, 201 and Figures 12a-c, 13a-f. &Lt; / RTI &gt;

13A, 13B, and 13E.

862, 870, 871, 872 (see Fig. 13C) from the pressure storage vessel 814 through the piston rods 873, 874, 875, 876, 877, Valve box 1160 includes 5x T-valves 1161-1165 (inclusive) that open to channel [817] for valve 818 and indirectly to communication 826 to valve 826. Pressurized return channels [825 and / or 828] from the pumps to the pressure reservoir 889.

The outlet of return channel 1150 from pump 1074 to pump 1151 is connected to storage pressure vessel 1075 by channel 1152. The pump 1151 may be connected to an external, sustainable energy source such as (not shown) and / or solar power (not shown) to the main axle 966.

11A-Z based on 19627 - 19618 base - 19617 (in main document 19601)

Figure 11A schematically illustrates the overall system for a motor ('green'), consistent with all requirements, as described in the Background of the Invention section. On the crankshaft 800 shown schematically, together with a U-shaped axle 801, axle bearings 802 and 803, is a piston rod 805 in which contraweights 804 are assembled, Which is connected to the inflatable piston 806 on the other side of the piston rod 805, which moves to the left ("L") (indicated by the arrows) from the first longitudinal position to the second longitudinal position, ("R") (indicated by arrows) from the longitudinal position to the first longitudinal position. The piston 806 may be moveably engageable with the inner wall 808 within the chamber 807. The chamber 807 has sections of continuously varying cross-sectional areas and the circumferences are different, and the inner wall 808 has a smaller circumference at the second longitudinal positions than at the first longitudinal positions. The piston 806 is produced so that the production size of the circumferentially untreated product is approximately equal to the circumference of the wall 808 of the chamber 807 at the second longitudinal position. The piston is connected to the piston rod 805 by the cap 809 while the flexible wall 810 of the piston 806 includes the reinforcement means 811 and the piston rod 806 is connected by the slidable cap 812, (805), which can slide on the piston rod (805). When the piston is disposed in the second longitudinal position and communicates with a pressure source, for example, a pressure valve 814, through the enclosed space 813, the piston 806 is moved by the fluid 822 The piston 806 will begin to move from the second longitudinal position to the first longitudinal piston position through the second enclosed space 815 in the crankshaft 800 (axle 801) Thereby causing the U-shaped axle 801 to rotate about the bearings 802 and 803. The movement will change the direction of movement of the piston 806 in the opposite direction, i.e., from the first longitudinal piston position to the second longitudinal piston position. The enclosed space 813 of the piston 806 may then communicate with the third enclosed space 816 in the crankshaft 800 (axle 801) (Which may also be a rotary pump, e. G. A centrifugal pump), which is connected to a crankshaft 820 having a U- shaped axle 821 by a piston rod 819 ). A crankshaft 820 may be connected to the crankshaft 800 so that the rotation of the U-shaped axle 801 causes rotation of the U-shaped axle 821 with the contra weights 834 . The communication reduces the pressure of the fluid 823 within the piston 806 and thereby reduces the circumference of the wall 808 so that the piston 806 moves away from the first longitudinal piston position in the second longitudinal direction So that it can be moved to the piston position. The fluid 823 becomes a reduced pressure (relative to the pressure of the fluid 822 of the piston when the piston is pressed in the first longitudinal position), and then the fluid 827 The pressure is of course also lower than the pressure of the fluid 822) and this is optionally transferred directly to the pressure vessel 814 through the channel 824 or is preferably transferred by the channel 825 to another piston pump And then the fluid 827 is pumped into the fluid 822 in the pump 826 and then to the pressure vessel 814 through the channel 828. The fluid 822 is then sent to the pressure vessel 814 through the channel 826. The fluid 822 is then sent to the pressure vessel 814. [ In addition, the pressure storage vessel 814 may be re-pressurized through the hose 2701 communicating with the pressure source. The fluid 822 is transferred from the pressure vessel 814 through the channel 829 to the second enclosed space 815. The piston pump 826 is electrically driven by the motor 830 through the other crankshaft 831. A motor 830 is connected by a wire 1069 to an electrical storage, e. G., An accumulator (or capacitor) storage type) 832 connected to the solar cell 833 It will be possible. An electric motor 830 may be used as a starting motor for rotation of the crankshaft 800. [ This may be done by clutch 836 (not shown). The crankshaft 800 may be connected to a flywheel 835 (not shown) and a gearbox 837 (not shown), the gearbox 837 may utilize hydrodynamic bearings for friction reduction . Bearings 833 for the crankshaft 821 of the piston pump 818. An alternator 850 communicates with the main axle 852 and charges the battery 832 through a connection 842. [ The configuration 851 of the auxiliary power supplies is shown in Figures 15a, 15b, 15c, or 15e. This battery 832 may also be charged by an external electrical power source 2700, for example, via a cable.

11B schematically shows control devices for the motor of FIG. 11A. Electric starter motor 830 includes a clutch (not shown), which couples axles 831 and / or 852 with an anker of an electric motor when the motor needs to be started. An electric switch 838 can be turned on and off by connecting the starter motor 830 to the battery (accumulator) 832, which is loaded by the solar cells 833 . The motor 830 may also be stopped when the pressure in the pressure vessel 814 reaches a certain maximum limit and the pressure measurement is made by the pressure sensor 839. [

The motor will also be able to start without using the starter motor 830, but with a simple opening of the reducing valve 840 in the channel 829. The further opening of this reduction valve 840 leads to a faster rotation of the crankshaft 801 and the lowering of the reduction valve 840 by a screwing down operation causes the crankshaft 801 to rotate more slowly . Closing the reducing valve 840 completely will stop the motor. The speed meter 841 communicates with the reducing valve 840. The alternator 850 communicates with the main axle 852 and charges the battery 832 through the connection 842. [ The configuration 851 of the auxiliary power supplies is shown in Figures 15a, 15b, 15c, or 15e.

Figures 11a-f (included) relate to a motor having a piston and a elongated cylinder in communication with the crankshaft, according to the consuming technique.

11C shows the actuator piston pressure management of Figs. 11A and 11B. At a point in time when the piston reaches the second longitudinal position from the first longitudinal position of the chamber - immediately after the direction of its movement is reversed - through the hole in the crankshaft, the second highly pressurized enclosure of the crankshaft Communication between the holes at the end of the piston rod with the space 822 and the enclosed space of the piston rod and accordingly with the internal volume of the piston through the hole 1101 is started, lt; / RTI &gt; As a result of the pressure, the piston will begin to move to the first longitudinal position, thereby turning the crankshaft and closing the hole, and thereby stopping the communication. Such movement reduces the internal pressure due to its increased internal volume, due to the fact that the elliptical piston begins to transform itself into a spherical shape. When the first longitudinal position is reached, there is still a mid-rate of pressure in the enclosed space within the piston and piston rod. When the piston reaches its first longitudinal position in the path returning to the second longitudinal position, immediately after its movement direction is reversed, the sealed space in the piston rod is displaced from the end of the piston rod Lt; RTI ID = 0.0 &gt; 1102 &lt; / RTI &gt; and a third enclosed space 823 in the crankshaft including the holes. The pressure inside the piston and the enclosed space is lowered to a certain minimum value (for example, the atmospheric pressure level), whereby the shape of the piston changes from spherical to elliptical. Due to the inertia of the crankshaft (or the driving force of another piston-chamber combination using the same crankshaft), the retracted piston will move to the second longitudinal position, and the process starts all over again.

Due to the communication between the enclosed space of the actuator piston and each of the second and the second enclosed spaces in the crankshaft, when the pressurized fluid needs to reach the piston, by the simple opening of the reducing valve, The piston may have to be stopped at a particular longitudinal position so that it can be moved again. This is because there is only one actuator piston-chamber combination on the axle crankshaft, where the piston can stop at the first longitudinal position and can be slightly retracted on the path to the second longitudinal position due to inertia Only if it will be a problem. The holes in the enclosed spaces may not be able to communicate with each other - the starting may only be possible by the starter motor.

The pressure drop in the piston may be caused by suction in the third enclosed space 823, which is caused by the piston pump 818, which takes fluid from the channel [817]. The pressure drop in the channel [817] may begin slightly before the actuator piston reverses its direction of travel from approaching the first longitudinal position to the second longitudinal position, thereby causing the enclosed space and the third enclosed When the holes in the space are open, the fluid may be sucked out of the enclosed space of the actuator piston. This means that the default angle between the crankshaft 801 of the actuator piston 810 and the crankshaft 821 of the piston pump 818 may not be zero. The main axle 852. Details of the assembly of the piston rod 805 and the U-bend axle 801 are shown in FIG. Details regarding the assembly of the piston rod 819 of the pump 818 with the crankshaft 820 are shown in Fig. Details of the guide portions of the connecting rod 925 and the piston rod 819 may be found in Section 19597 of this application.

As another preferred detail: from the second enclosed space 822 of the crankshaft 800 to the space 813 of the piston rod 805, preferably with two valve actuators according to either 210f or alternatively 210e, There may be a combined assembly comprising two check valves and the assembly is moved from the space 813 of the piston rod 805 to the third enclosed space 823, Lt; RTI ID = 0.0 &gt; valve &lt; / RTI &gt; There are also two separate assemblies, each including a check valve 522 having a sub-assembly 520 comprising a valve actuator according to Figures 304 and 301, From the enclosed space 822 to the space 813 of the piston rod 805 and the assembly in the opposite direction from the space 813 of the piston rod 805 to the third enclosed space 823, Includes a check valve 522 having a sub-assembly 520 including a valve actuator according to FIG.

11D shows an assembly of the U-bend axle 801 and the piston rod 805 of Fig. 11C and is shown at a particular point in time when the piston rod 805 and U-bend axle 801 are turned to each other have. Using the O-rings 1104, 1104 ', 1104 ", and 1104 "between the bearings 1100, 1100' and 1100 " and the piston rod 805 and the axle 801, Is assembled on the U-bend axle 801. The enclosed space 813 is in fluid communication with the third enclosed space (with the fluid 823) through the hole 1102 816. A second enclosed space 815 having a fluid 822 communicates with the flow blind hole 1101 and thus does not communicate with the enclosed space 813. [ The flow hole 1102 separates the second enclosed space 815 from the third enclosed space 816. At another point of time the flow hole 1102 becomes a clogged hole while the flow- The holes 1101 and 1102 never communicate with the enclosed space 813. The base 926 of the piston rod 805 includes two portions 927 and 928, Of the channels 822 and 823, An axis 929 is located within the separation surface (not shown) of the base 926. Two bolts 930 and rings 931 on each side of the piston rod 805 are located in two portions 927 And 928 together.

Fig. 11E shows the details of the joint of the piston rod 805 and the connecting rod 925, 805 'shown in Fig. 11C. The piston rod 805 has an end portion 932 having an end communicating with the second enclosed space 815 and the third enclosed space 816 on one side and the enclosed space 816 of the piston 810 on the other side. And a channel 933 communicating with the space 813. Between the holes 945 in the outer wall 943 of the end portion 932 of the piston rod 805 and the holes 946 in the inner wall 944 of the connecting rod 925, ). An end 942 of the connecting rod 925 includes an O-ring 939 that seals the end 942 against the end 932 of the piston rod 925. The axle 940 is reliably connected (does not move) into the end portion 932. The end portion 932 of the piston rod 805 includes two portions 934 and 935 which are fastened together by bolts 936 and washers 937 one on each side of the centerline 938 of the assembly do. The connecting rod 925 can turn the end 947 of the axle 940. To create the shoulder 953, the end 947 has an increased diameter relative to the diameter of the axle 940. Portions 934 and 935 of end 925 have 90 ° bearings and such bearings are also bearings for movement of end 942 over end 932. O-ring 950 seals axle 940 on hole 947 of connecting rod 925.

Fig. 11f shows the U-shaped axle 801 and the details of the channel (e.g., 823) inside the crankshaft shown in Figs. 11a-c. During the manufacturing process of the crankshaft 801, after the preliminary hole is made by forging, the channel 823 may be drilled. Such drilling may leave holes within the outer walls 952 of the crankshaft 801 and these holes may be closed by any means, such as welded rods, sealed threads, A pin 954 having a head 955 is shown in the drawing, which fits very well with respect to the holes in the wall of the crankshaft where the space between them is filled by hard solder . Proper balancing of the crankshaft 801 at the end of the production process is important.

Figures 11g-w (included) relate to a motor having a piston in communication with a crankshaft and at least one elongated cylinder, in accordance with closed space volume technology (abbreviated as "ESVT").

Figures 11g and 11h illustrate the basic ESVT in two variants relating to the pressurization of the storage pressure vessel, in which the pumps controlling the volume of the enclosed space are driven by a two-way actuator. The different power lines are clearly shown and separate the use of power generated by the auxiliary power supplies.

Figure 11g shows a cross-sectional view of the embodiment of Figure 11A, which is adapted to the ESV-technique, with U-shaped axle 801 ', piston rod 805 and inflatable actuator piston 806 including two contra weights 804, Fig. One end of the axle 801'may be connected to the electric starter motor 830 and the electric starter will be able to acquire energy from the accumulator 832. The accumulator may be connected to the solar cell 833 and / Or any other preferably sustainable (or alternatively, non-sustainable) power source (see FIGS. 15A-F). At the other end, the axle 801 'may be connected to a flywheel 835 (not shown), a clutch 836 (not shown), and optionally a gearbox 837 (not shown).

A channel 1050 in continuous communication with the ESVT pump 1055 is located within the U-shaped axle 801 'and the ESVT pump includes a piston 1061 (see, for example, Figs. 50-52 And a conical chamber 1062, which con- trols over-pressure on the overall pressure within the channel 1050. The conical- The overpressure controls the speed of the motor. The movement of the ESVT-pump 1055 is generated by a two-way actuator 1053 and the actuator is controlled by two reduction valves 1057 and 1058, Adjust the pressure at one side of the piston (not shown) inside direction adjuster 1053; The reduction valve 1057 communicates with the one side of the two-way actuator 1053 by the channel 3300 and the reduction valve 1058 communicates with the other side of the two-way actuator 1053 by the channel 3301 Communicate. The reduction valves 1057 and 1058 are preferably interconnected electrically (and optionally mechanically-there are other solutions, but not shown) so that the pressure build-up in one (the piston's one side) (The other side of the piston) will result in simultaneous pressure reduction and vice versa. The reduction valve 1057 is controlled by the speed meter 841 through the control device 840 '. The reduction valves 1057 and 1058 communicate with the pressure storage vessel 890 via a feeder line [829]. The pressure storage vessel 890 may be pressurized by the fluid 1063 when the motor is produced.

In addition, the channel 1050 continues to communicate with the piston rod 805 of the ESVT-pump 1055. See FIG. 11t for details regarding assembly of the axle 801 'and the connecting rod. Thus, a change in the volume / pressure of the ESVT-pump will result in a change in volume / pressure within the actuator piston 806, thereby resulting in a change in the movement of the actuator piston 806.

An ESVT pump 1056 comprising a piston 1059 (shown for example in accordance with Figures 50-52 (inclusive) and a conical chamber 1060) is driven by a two-way actuator 1072, To adjust the pressure of the channel, thereby causing the actuator piston 806 to change in volume at a particular longitudinal position, according to Figures 10a-f. The two-way actuator 1072 is driven by the two-way actuator 1053 by the reduction valves 1051 and 1051 in the same manner as the ESVT-pump 1055. However, the reduction valve 1051 is controlled by the sensor 1064 and communicates the rotational position of the axle 801 to the reduction valve 1051, thereby causing the piston 806 ) Will expand and contract at the correct time. Reduction valves 1051 and 1052 may communicate with a pressure source, such as pressure storage vessel 890, for example. The other side of the enclosed space will be able to communicate with the enclosed space 813 of the piston 806 continuously. The reduction valves and associated equipment are in electrical communication with the battery 832 through a wire 1069.

11H shows the configuration of FIG. 11G (with the components having the reference numbers referenced in FIG. 11G), wherein a pump 826 for re-pressurization of the pressure storage vessel 890 has been added, The cascade is the same as that shown in FIG. 11A, but the pump 820 is redundant, which, at the correct time, provides a low pressure in the third enclosed space, This may be necessary for 'consuming technology' to enable decompression, but it may not be needed in current ESV technology. Can be connected to the feeder line 825 of the piston pump 826 when the outlet [1070] of the 2-way actuator 1072 is in communication with the pump 820, but the pump 820 is not present. The required check valves are not shown. This' consumption 'configuration of the two-way actuators 1053 and 1072 is such that each of the inlets of the two-way actuators 1053 and 1072 can be coupled to the interior of the piston (the two-way actuator 1053' 1052, 1057 and 1058, respectively, communicating with the spaces at both sides of the pressure storage vessel 890 (see FIG. 11 for a schematic diagram), and a pump 826 Are the spaces in both sides of the piston inside the chamber of the two-way actuators in direct communication. The required check valves are not shown. When one valve is more open, each of the reduction valves 1057-1058 and 1051-1052 is related to each other in such a way that the other valves are closed at the same time. The valve means 840'of the reducing valve 1057 is activated by the speedometer 841 while the reducing valve 1051 is activated by the sensor 1064 in communication 1054. The reduction valves are electrically activated via wire [1069].

An alternator 850 communicates with the main axle 852 and charges the battery 832 via connection [842]. The configuration 851 of the other auxiliary power supplies is shown in Figures 15a, 15b, 15c, 15e, or 15f. The pump 826 will also be able to communicate with a flywheel (not shown) and / or a regenerative braking system (not shown). As shown in the figures, other auxiliary power sources may be used: preferably according to Figures 15a, 15b, 15c, 15e, 15f and optionally non-sustainable power supplies.

11i-11n (inclusive) illustrate one (Figs. 11i, 11k, 11m) and two cylinder motors (Fig. 11j, 11l, 11n), respectively, wherein the motors comprise main components For example axles and belts / gears, for example). The ESVT pump for controlling the volume of the enclosed space is provided by a two-way actuator (Figs. 11i and 11j), a crankshaft (Figs. 11k and 11l) or a camshaft (Figs. 11m and 11n) Power is supplied. Due to the different sizes of loops of the power types, the conical cylinders may have different sizes for each power type. The auxiliary power supplies are referred to by reference only. Other auxiliary power sources may be used, as shown in the Figures: preferably according to Figures 15a, 15b, 15c, 15e, 15f and optionally non-sustainable power supplies. Each figure comprising two cylinder motors consists of an enlarged view of "left" and "right ".

Figures 11i-11r (included) show several configurations of one cylinder motor, and two cylinder motors. One of the purposes is to show the clear updividing of the power delivered, the power used - also schematically disclosed in FIG. Another object is to show the differences between controlling the pressure build-up of the actuator piston (s) by either one of the wires that can communicate with the transmitted power, by the camshaft or by the crankshaft will be. In order to improve the efficiency of the transmitted power, Figs. 11 o-11 r illustrate the use of H ₂ as a power source (preferably derived from the hydrolysis of H ₂ O), preferably in direct communication with the camshaft or crankshaft, A small combustion motor is shown. Several configurations of such combustion motors are shown. Another purpose is to show how the cylinder-by-cylinder pressure control means can be combined or not combined with more than one cylinder motor-first, under the conditions of the combined crankshaft, how the subsequent cylinders work together 17A, bh (inclusive), in which the power strokes of one of the two cylinders of the same motor are made simultaneously with the return stroke of the other cylinder (serial power), while FIG. The power strokes of two cylinders of the same motor at 18a-g (inclusive) are functioning simultaneously (parallel power). Thereafter, it will be possible to determine what pressure control means (e.g., ESVT pumps) can or can not be combined for the two cylinders, and power lines (e.g., , Crankshaft) can be combined or not.

Figure 11i illustrates the use of a two-direction actuator 1072 for driving the ESVT-pump 1056, which controls the size of the enclosed space 1050 + 813 and functions as shown in Figure 11h, Chamber combination 800 'based primarily on the concept shown in FIG. Actuator 1055 (piston 1061, chamber 1062) controls the speed of the motor. All references relating to the presence or absence of pump 820 in the description of FIG. 11h are also valid here.

Only new problems will be covered here.

Reference is made to Fig. 11S for details of assembling the actuator 1055 onto the axle 852. Fig. The upper end portion 1130 of the chamber 1062 of the actuator 1055 is mounted on the motor main frame 5000. The arrangement of the communication between the enclosed space 1050 of the axle 852 and the chamber 1062 can also be seen in Fig.

The actuator 1053 'that varies the speed of the motor is partially configured and operates in a manner different from the actuator 1053 shown in FIG. 11H because the actuators 1053 and 1072 have different functions to be. In the configuration shown in this figure, the actuator 1053 'is mounted on the opposite side of the piston 1078 in the chamber 1079, which communicate with each other through a large number of check valves (not shown here) Each of the spaces 1075 and 1076 - see Figures 16a-c (inclusive) for details. Therefore, there is no return flow from the spaces 1075 and 1076 to the pressure storage vessel 890 through the pump 826. [ This will reduce energy.

Each of the spaces 1075 and 1076 communicates with the reduction valves 1058 and 1057, respectively. The chambers may additionally communicate with each other through each of the valve actuator arrangements 1121 and 1122 shown in Figure 304 and, as needed, they may additionally be controlled in accordance with Figure 211e or 211f. The valve actuator arrangements 1121 and 1122 are arranged in opposite directions to each other. A chamber 1079 of the actuator 1053 'is mounted on the motor main frame 5000. More details are shown in Figures 16a-b.

An ESVT-pump 1056 includes a chamber 1060 and a piston 1059 and is mounted on the main axle 852 - see Figure 11u for suspension detail parts. The two-way actuators 1053 and 1072 are driven by the compressed fluid 1063 stored in the pressure storage container 890. The reduction valve 1051 is activated by the communication line 1054 and the power line 1069 via the electric regulator 1065. [

The pump 826 of Figure 11h is configured in detail in Figure 11v. The pump acquires energy from an electric motor 830 ', which receives electricity from the battery 832 through electrical communication [1080]. The circular movement of the axle of the motor 830 'is converted into a translational motion and a partial rotation by a kind of crankshaft 1217. [ When the pump 820 is not present, the flow from the two-way actuator 1072 will be communicated to the pump 826 by the channel 1083. The compressed fluid flows from the pump 826 to the pressure storage vessel 890 through the channel [828]. An alternator 850 communicates with the main axle 852 via the toothed belt 1073 and the wheels 1074 and 1077. The alternator delivers electrical power to the battery 832 through electrical communication 842. The electric drive system 830 is similar to the elements in FIG. 11A.

Figure 11j shows a schematic view of two cylinder motors, while special ones are shown enlarged in Figures 11ja and 11jb.

Fig. 11J shows two cylinder motors constructed in part, based on the concept shown in Fig. 11I. The specials are shown in the case of a combination of two crankshafts and have the advantage of one component for a plurality of similar tasks. There are two cylinder motors instead of many of those last mentioned, which is due to the example shown here, wherein, in the same moment (asynchronous crankshaft design) according to FIG. 17b, the two actuator pistons are in the same longitudinal direction Location. Each of the "cylinders" more clearly marked as a "chamber" is hereinafter referred to as a "chamber", separated from each other by, for example, a tightening rod 1270 (FIG. 11x) between the channels of each sub- Lower crankshaft &apos;, which is enclosed within the crankshaft.

Thus, each actuator piston has an ESVT-pump that controls the volume of each enclosed space, while each ESVT-pump is driven by a two-way actuator. As the actuator pistons must move in a (non) synchronous manner, the pressure relief valves of each two-way actuator may need to communicate, for example, electrically, with one another 1066 for synchronization purposes. However, the pressure relief valves will also be able to communicate through the sub-crankshafts, respectively, by the sensor measuring the rotation of each sub-crankshaft 1064. Whether two ESVT-pumps can be combined or not combined can not be concluded without substantial investigations: see Figures 17c-17h (inclusive).

There are, therefore, two speedometer-actuators that must communicate with each other 1067. This may be accomplished through a speedometer 841 - one speedometer for electrically controlling the positive pressure reduction valves of each two-way actuator 1057, for example. Whether two two-way actuators can be combined or not combined into one can not be concluded without substantial investigations: see Figures 17c-17h (inclusive).

Ex. There may be two or only one pressure reservoir which is pressurized by the operations and repressed during operation by the pump. Ex. There may be one pump that can be powered by electricity from the battery 832 that is charged by operations and which can be recharged during operation by an alternator 850 in communication with the main motor 852 . In addition, such a battery may be charged by an external electrical power source, for example, via a cable. Pressure reservoir 890 via a hose, preferably in communication with a pressure source such as a medium pressure canister or alternatively a high pressure canister or an external pump (e.g., driven by a windmill) It will be possible. At least one of the auxiliary power supplies according to Figures 15a, b, c, e, f will be able to charge the batteries.

First, when there are three or more preferably four and even more pairs of cylinders in one motor, the inlet / outlet of the two-way actuators for speed control and the inlet of the ESVT-pumps / Outlet, so that the total number of the two-way actuators and pumps can be reduced. See Figures 17c-17h (inclusive).

The pump 820 may become redundant.

The two sub-crankshafts on the main motor axle are arranged in the plane of the central axis of the crankshaft in order to compensate for possible timing differences of changes in the shapes of the actuator pistons due to elastic characteristics of the walls of the actuator pistons during re- 11w, 11w ', 11x, which may have some flexibility within a plane perpendicular to the plane of the connector.

Figure 11ja shows an enlarged view of the left part of Figure 11j.

Fig. 11Jb shows an enlarged view of the right part of Fig. 11J.

Fig. 11k shows one cylinder motor, based on the concept shown in Fig. 11h, in which a secondary crankshaft is used instead of a two-way actuator to drive the ESVT-pump. The auxiliary crankshaft is driven by an electric motor, which is powered by a battery. The battery is recharged during operation by an alternator in communication with the main motor axle. Due to the need for both controls for co-ordinating the speed of the speed-actuator with the speed of the ESVT-pump: the speedometer 841, the pressure reducing valve 1057 and the electric motor 3500 are connected to the electrical / And are communicated with each other by a wire 3501 through an electronic regulator 3502. A motor 3500, also shown in Figures 11l, 11m and 11n below, is coupled to the crankshaft 3503 through wheels 3506 and 3507, for example, toothed belt 3505, which drives the ESVT pump 1056, . The electric motor 3500 is connected to the battery 832 by the wire 3504 through the regulator 3502. [

The fact that the (auxiliary) crankshaft, which is mounted on the fixed crankshaft axis, is used to drive the ESVT-pump, the piston rod of the ESVT-pump is connected to the crankshaft (as seen in Figure 11c for the actuator piston) Or a similar oscillation configuration of the pump shown in Figure 11V is used where the connecting rod is not present and wherein the top portion 1130 and the piston rod The chamber 1060 of the ESVT pump turns on the crankshaft in communication with the main axle 852. Assembly of the ESVT-pump on the main axle is the same as if the pump did not vibrate (see, for example, Fig. 11u, but the fitting at the lower end of the pump for the axle may be slightly larger).

Since the two-way actuator of the ESVT-pump has been replaced by the auxiliary crankshaft, and the pressure storage vessel, which may require limited repressurization, is kept pressed, the two-way actuator does not require repressurization The pump 826 may be smaller than that shown in Figure 11i. While this is the preferred solution, while the solution has the pump 820, the pump 826 becomes an extra solution.

FIG. 11I shows a schematic view of two cylinder motors, while special features are shown in enlarged FIGs. 11a and 11lb.

FIG. 11L shows two cylinder motors, based on the concept shown in FIG. 11K, in which each cylinder has a space sealed therein, whereby the ESVT-pump controls its respective volume, Are driven by the same auxiliary crankshaft axle.

Due to the need for both controls for adjusting the speed of the speed-actuators and the speed of the ESVT-pump: when both ESVT-pumps use the same axle including both crankshafts, the speedometer 841 / The motor 1057 and the electric motor 3500 communicate with each other.

Since the two-way actuator 1072 of the ESVT pump has been replaced by the auxiliary crankshaft - this could be made as a single piece due to the fact that the assembly of the connecting rod and the crankshaft is simple (no channel) - Due to the fact that the two-way actuator 1053 may not require repressurization, instead of holding the pressure storage vessel under pressure, which may require limited pressurization, It will be smaller than the While this is the preferred solution for two cylinder motors, while the solution has a pump 826, the pump 820 can not be selective.

Fig. 11la shows an enlarged view of the left part of Fig.

FIG. 11Ib shows an enlarged view of the right part of FIG.

Fig. 11m shows one cylinder motor based on the concept shown in Fig. 11h, which uses a camshaft to drive an ESVT-pump, instead of a two-way actuator.

The camshaft is driven by an electric motor powered by a battery. The battery is recharged during operation by an alternator, in communication with the main motor axle. Due to the necessity of both controls for adjusting the speed of the speed-actuator and the speed of the ESVT-pump: In the same manner as shown in Figure 11k, the speedometer 841, the pressure reducing valve 1057 and the electric motor 3500 communicate with each other.

The camshaft 3515 has a limited height of the cam 3516 for raising the piston rod of the ESVT-pump 1056, which has a reduced stroke length and the ESVT- Which means that it has a width of the aid chamber increased than that of Figures 11k and 11l. In order to allow the piston to reverse the movement of the piston, initiated by the cam, an additional spring may be required.

Since the two-way actuator 1072 of the ESVT pump has been replaced by the auxiliary crankshaft and instead of holding the pressure storage vessel under pressure which may require a limited pressurization, Due to the fact that pressurization may not be required, the pump 826 may be smaller than that shown in Figure 11i. While this is the preferred solution, while the solution has the pump 820, the spare pump 826 becomes an optional solution.

Figure 11n shows a schematic view of two cylinder motors, while special considerations are shown in enlarged Figures 11na and 11nb.

11n shows two cylinder motors based on the concept shown in Fig. 11m, wherein each cylinder has a space sealed therein, whereby the pump controls its respective volume, and the two are identical And is driven by the camshaft.

Due to the need for both controls for the speed of the speed-actuators and the speed of the ESVT-pumps: when both ESVT-pumps use the same crankshaft axle, the wire [3501 , The speed meter 841 / pressure reducing valve 1057 and the electric motor 3500 communicate with each other.

Since the two-way actuator 1072 of the ESVT-pumps has been replaced by the camshaft and instead of holding the pressure storage vessel under pressure which may require a limited pressurization, the two-way actuator 1053 is re- The pump 826 may be smaller than that shown in Figure 11i. While this is the preferred solution for two cylinder motors, the solution may have a pump 826 while the pump 820 may not be selective.

Fig. 11na shows an enlarged view of the left part of Fig. 11n.

Fig. 11nb shows an enlarged view of the right part of Fig. 11n.

Each of Figures 11o, 11p and 11q and 11r (inclusive) relates to configurations of Figures 11k and 11l (crankshaft) and Figures 11m and 11n (camshaft), respectively, wherein an auxiliary power source is connected to solar cells 833 ), Which is preferably produced by electrolysis from the conductive H ₂ O (and from the canister under pressure - cooled or liquefied or otherwise), preferably H ₂ (And optionally any other suitable combustible power source), the combustion motor 3525 communicates directly with the ESVT-pump, which controls the volume of the enclosed space. Instead of the configuration of Fig. 15C, other configurations such as the configuration of Fig. 15D may be used. The fact that the combustion motor directly drives the power lines (ESVT-pump (s)), the crankshaft / camshaft, instead of the first generation electricity to drive the electric motor means about four times more efficient . Each drawing shows a different type of cooling for a combustion motor. A fluid (e.g., air) heated by the combustion motor may be used for heating purposes, for example to heat compartments (indoors) of a vehicle.

Figure 11o shows one cylinder motor, based on the above concepts, using a crankshaft for driving an ESVT pump. Only new problems will be covered here.

In order to properly operate the motor, it is necessary to synchronize several parts in the motor.

And burnt motor, the crankshaft drive, ESVT- pump that drives the electrolysis of H ₂ O resulting in a H ₂ O _2, and the specific volume used for,

The communication between the two-way actuator for the speed actuator and the ESVT-pump has been dealt with in the description of Figs. 11k, 11l, 11m and 11n.

The motor also drives the pump 826 shown in FIG. 11V for re-pressurization of the pressure storage vessel 890 through the toothed belt and wheels.

The configuration of the auxiliary H ₂ combustion motor (according to FIG. 15C) is shown in FIG. 15C together with the filler opening 1614 and the outlet channel 1615 for the container 1616 in which the electrolysis 1617 of the water 1613 is generated, And a storage tank 1612 for conductive H ₂ O 1613 (H ₂ O from tap water and conductors, for example, salt or simple seawater). Wire [3547] connects speed meter 841 with regulator 3509 to control the production levels of H ₂ and O ₂ through electrolysis. Check valves are not shown. An electrical power line [3547] is connected from the battery 832 to the vessel where electrolyzations are generated. The resulting H ₂ was transferred to the motor by a pump and did not show very essential check valves. The resulting O ₂ is also transported to the motor by the channel + pump [3546] - it does not show the very essential check valves - it is used as a kind of turbo. The H ₂ motor 3525 is shown to be air-cooled in this view wherein the heat exchanger 3539 is connected to the heat exchanger 3539 for purposes of heating (arrows 3540) the vehicle's cabin. Directly or indirectly by the liquid, warm air is transported through the channel [3538].

FIG. 11P shows a schematic view of two cylinder motors, while special features are shown in enlarged FIGs. 11Pa and 11Pb.

Fig. 11P shows two cylinder motors, based on the concept shown in Fig. 11O, in which each cylinder has an enclosed space, and thus an ESVT-pump, both of which have the same crankshaft and two Speedometer actuators, but driven by one auxiliary motor. The crankshaft is driven directly through the gear wheels 3526 by a liquid cooled combustion motor using H ₂ , which is induced by electrolysis of H ₂ O. The crankshaft drives the ESVT-pumps and the pump 826 to re-pressurize the pressure reservoir 890. The shown tooth type belt 3527 can be replaced by gear wheels.

There is a water pump 3528 for circulating the cooling water 3529 from the radiator 3530 that is air cooled and to the other radiator 3531, It will be able to warm up the air of. The water pump communicates with an alternator 850 that recharges the battery 832 as well as the main axle 852 of the motor.

Fig. 11 pa shows an enlarged view of the left part of Fig. 11P.

FIG. 11Pb shows an enlarged view of the right part of FIG. 11P.

Figure 11q shows one cylinder motor based on the above concepts, using a camshaft to drive an ESVT-pump. The principle of the camshaft of Figure 11q is the same as that of Figure 11m. The camshaft is directly driven by the auxiliary power from the forced gas (e.g., air) cooling combustion motor. A pump for repressurizing the pressure storage vessel is directly driven by the combustion motor. Batteries 832 are charged by an alternator mounted on the main motor axle, or according to Fig. 15d.

Fig. 11r shows a schematic view of two cylinder motors, while special features are shown in enlarged Fig. 11ra and Fig. 11rb.

Fig. 11r shows two cylinder motors based on the concept shown in Fig. 11q, in which each cylinder has an enclosed space and an ESVT-pump for controlling its volume, both of which have the same crankshaft . The overall concept can be seen from the preceding figures.

Fig. 11 (a) shows an enlarged view of the left part of Fig. 11 (r).

Fig. 11 (r) shows an enlarged view of the right part of Fig. 11 (r).

Figures 11s-w (inclusive) show specific parts of some components, which were used in Figures 11a-r (inclusive).

Fig. 11s shows the details of the joint of the pump 1061 of the piston-chamber combination according to Figs. 11i-11r with the main axle 852 of the motor, using ESV technology. The base 1140 of the pump 1061 is provided with two base portions (not shown) that are bolted together by a washer 1144 and two bolts 1143, around a properly suitably fitted main axle 852 1141 and 1142, respectively. The base portion 1141 is bolted onto a motor housing 1145 having a bearing 1146 around the main axle 852 that is turned around. The motor housing is shown as a hatch 5000. The base portions 1141 and 1142 have an O-ring 1148 that seals the sliding connection between the main axle 852 and the base portions 1141 and 1142. The pump chamber 1149 communicates with the third enclosed space 1150. Bolts 1151 and washers 1152.

Figure 11t illustrates the use of ESV technology to provide a continuous communication between the enclosed space 813 of the actuator piston 806 and the channel 1050 of the crankshaft 801 ' Shows the details of the joint of the crankshaft 801 'on the main axle 852 of the motor and the connecting rod 805' of the actuator piston 806.

At a particular point in time, the assembly of connecting rod 805 'and U-bend axle 801' of Figures 11g-11r is shown. The connecting rod 805 'and the U-bend axle 801' turn over each other. On the U-bend axle 801 ', using the bearings 1100 and 1100' 'and the O-rings 1104 and 1104' 'between the connecting rod 805' and the axle 801 ' (805 ') is assembled. The enclosed space 813 communicates with the channel 1050 through the holes 1106, 1107 and 1108. In order to avoid stresses in the axle 801 ', there are two holes at a certain distance from each other, on different circular positions on the outer periphery of the axle 801'. The channel 1050 continuously communicates with the holes 1106, 1107 and 1108 through the open spaces 1105 and 1105 'together with the enclosed space 813. This results in continuous communication between the channel 1050 and the enclosed space 813 of the actuator piston 806. The base 926 'of the connecting rod 805' includes two portions 927 'and 928' wherein the central axis 929 of the channel 1050 is spaced apart from the separation surface 926 ' (Not shown). Two bolts 1110 and rings 1111 on each side of the piston rod 805 'hold together the two portions 927' and 928 '.

Fig. 11u shows the details of the joint of the pump 1060 in the piston-chamber combination according to Figs. 11i-11r with the main axle 852 of the motor, using ESV technology. The base 1180 of the pump 1060 has two base portions 1181 and 1182 which are bolted together by a washer 1184 and two bolts 1183 around a properly suitably fitted main axle ). The base portion 1181 is bolted onto a motor housing 1185 having a bearing 1186 around the main axle 852 that is turned around. The motor housing is shown as a hatch 5000. Base portions 1181 and 1182 have an O-ring 1188 that seals the sliding connection between the main axle 852 and base portions 1181 and 1182. And the pump chamber 1189 communicates with the second enclosed space 1190. Bolts 1191 and washers 1192.

FIG. 11V shows the pump (e. G., 826) of FIGS. 11H-11R and the mechanism for driving its base.

The pump 1200 includes a chamber 1201, a wall 1206 of the chamber 1201, a base 1202, and a top portion 1203. The piston 1204 is of the type described in section 19640 herein, and a pressure measurement sensor 1205 is located at the end of the piston rod 1214. A bearing 1207 in the upper end 1203 of the pump 1200 is preferably manufactured in accordance with section 19597 herein-meaning that the bearing 1207 can withstand the greater lateral forces from the piston rod 1214 . The base 1202 of the pump 1200 can rotate around the axle 1208 within the boundaries 1222 of the other base 1209 that are part of the motor housing 1210 - have. A contra weight 1212 is assembled on the side base 1202 at the opposite side of the axle 1208 to the chamber 1201 of the pump 1200 so that the center point 1213 of the axle 1208, Lt; RTI ID = 0.0 &gt; 1200 &lt; / RTI &gt; The pump 1200 includes a piston rod 1214 that is guided by the bearing 1207 in the upper end 1203 of the pump 1200. A piston 1204 is assembled to one end of the piston rod 1214 while an axle 1216 is assembled to the other end of the piston rod 1214. The axle 1216 is disposed perpendicular to the piston rod 1214 and the piston rod 1214 is mounted on the axle 1216. The disk 1217 is positioned a-centrally on the disk 1217, preferably proximate to the side 1219 of the disk 1217, And a bearing 1218, The disk 1217 rotates about the disk axle 1220 in communication with the electric motor 1221. The rotation of the axle 1220 causes the disk 1217 to rotate so that the axle 1216 rotates non-centrally about the axle 1220 in a plane perpendicular to the disk 1217. This is because the piston rod 1214 is translationally moved from the upper end 1203 to the upper end 1203 of the pump 1200 while the angles s and t in relation to the central axis 1223 of the pump 1200, The piston rod 1214 rotates the chamber 1201 of the pump 1200 from one boundary 1222 to another boundary and vice versa. This causes the piston 1204 to move within the chamber 1201. An inlet 1224 and an outlet 1225 (not shown) of the pump 1200 are part of the base 1202 of the pump 1200 by the use of the piston 1215 type, And the inlet 1224 and outlet 1225 may comprise check valves. The medium (1226) of the pump (1200). When different types of pistons are used, the positions of the inlet 1224 and the outlet 1225 may be different from the above positions.

Fig. 11w shows the connecting joint between two crankshafts of a two-cylinder motor according to Figs. 11j, 11l, 11n, 11p, 11r. The joint joint shown is an improved version of the version shown in Figures 11j, 11l, 11n, 11p, 11r. In these drawings, the versions of such connection joints are shown, wherein the adjacent enclosed spaces communicate with each other. A crankshaft 1250 of the left side of the cylinder (not shown) includes a channel 1251, which serves as a (second) enclosed space. The ends 1253 of the crankshaft 1251 are assembled so as to face the end 1254 of the crankshaft 1252 of the right side of the cylinder (not shown), wherein both crankshaft ends 1253 and 1254 Within each of the flanges 1256 and 1257, the gasket 1255 is compressed ("buried") between the ends 1253 and 1254 in three directions. The last mentioned crankshaft 1252 includes a channel 1265, which functions as a (third) sealed space and communicates with the right side of the cylinder (not shown). Each of the flanges 1256 and 1257 preferably includes an odd number of holes, and a hole 1258 is shown. In the hole, a thin flexible cylinder 1259 is fit tightly fitted to the hole 1258. In the cylinder 1259, a bolt 1260 is arranged to be passed through. This thin flexible cylinder 1259 allows for a very small difference in the angular position of the two assembled crankshafts 1250 and 1252, and the difference is due to the asynchronous movement of the actuator pistons (not shown) , Non-synchronization. Washer 1261 and nut 1262.

FIG. 11w shows an improved seal (with respect to the gasket 1255) of the gasket 1263. Flange 1256 has a cavity 1264 while flange 1257 has a hump 1265 (not shown) and is fitted into cavity 1264. When the connection is flexible, an alternative for tightening is shown wherein the flange 1257 is flat.

Figure 11x is the same as Figure 11w except that no communication between the channels is possible because the tightening load 1270 is placed in the channels 1271 and 1272 and the common channel portion of each of the channels 1273 and 1274 have larger diameters, in order to obtain shoulders 1275 and 1276. [ The tightness of the tightening rod 1270 in one of the channels 1273 or 1274 is obtained, for example, by suitable fittings and soldering in one of the ends. Improved sealing of the gasket 1263 - this configuration is identical to that shown in Figure 11wa.

Instead of the toothed belts at the power side of the motor according to Figures 11d-w, they may be exchanged very well by the gear where the pump (s) is driven.

Fig. 12A shows a configuration 800 of the motor according to Fig. 11B, in which the piston-chamber combination communicates with the main axle via a crankshaft and in this figure, according to Fig. 10A or 12B, , And wherein the suspension of the piston is shown in FIG. 12C. FIG. &Lt; RTI ID = 0.0 &gt; 12C &lt; / RTI &gt; There is shown a 'black box' for the outlet communicating with the pump 818 through the channel [818] for the inlet communicating with the reducing valve 840 through the channel [.....]. The reduction valve 840 is controlled by a speedometer 841.

12B shows the motor, wherein the piston of the actuator piston-chamber combination moves and the chamber does not move. The motor includes a chamber 960, which includes four sub-chambers 961, 962, 963 and 964, each of which is connected to the same central axis 965 Which has an axle 966 through the center 967 of the chamber 960. A piston 968 is disposed within each of the sub-chambers 961, 962, 963, and 964, and a piston 968 is disposed within each of the sub-chambers 961, 962, 963, and 964, Chamber 961 ' when in the second rotational position of lower-chamber 961, which is contiguous with position 968 &apos; and with sub-chamber 964, The first rotational position of the sub-chamber 964 is located closest to the second rotational position of the lower-chamber 961 and has the smallest diameter in the second rotational position. The actuator piston 968, There are shown four holes 970 for rotating clockwise about an axis 966 and for assembling the chamber 960 on the axle 966.

The piston 968 'and 968 "(two different &lt; RTI ID = 0.0 &gt; Enclosed space 1070 of the same size piston is terminated at axle 966 and is sealed with two O-rings 1071 disposed on each side of the enclosed space 1070 . The enclosed space 1070 communicates with the second enclosed space 1072 in the axle 966 where it terminates in the housing 1073 where there is a T-valve 1074 ' The T-valve controls the entry of the fluid 822 through the channel [829] and the reducing valve 840 from the pressure reservoir 814. The fluid 822 controls the pressure within the pistons 968 'and 968 ". The discharge from the pistons 968' and 968 "consists of a cascade of pumps through the channel 817 Or rotational).

An electrical signal 1076 communicates with the electrical / electronic control unit 1077, which controls the T-valve 1074 'in the housing 1073 via signal [1078]. Thereby, rotation of the axle 966 controls the T-valve 1074 ', thereby controlling the pressure in the pistons 968' and 968 ". From the pressure source 1075 to the control unit 1077 The flange 1079 connects the chamber 960 to the suspension 1080 mounted on the axle 966. Belt 1081. For example, There may be a pump as the pump 821 'and / or 826', but not shown in this figure - the pump communicates with the pressure source 1075. The pump will be able to communicate with the axle 966 . In addition, the pump will be able to communicate with the flywheel and / or regenerative braking system 1082.

12D (enclosed space) shows the AA section of FIG. 12B, the chamber 960 is immovable and the pistons 968 'and 968 "are movable. The encapsulation of the pistons 968' and 968 & The closed space 1070 is terminated at the axle 966, where it is sealed with two O-rings 1071. The enclosed space 1070 communicates with the second enclosed space 1072 in the axle 966 where it terminates in the housing 1073 where the piston-chamber combination 1074 is present, The combination controls the pressure inside the pistons 968 'and 968 " (the same piston of two different sizes). The piston-chamber combination passes through the channel 890, the fluid 889 of the power source 1075, Lt; / RTI &gt;

Electronic control unit 1077, which controls the piston-chamber combination in housing 1073 via signal [1078]. Thereby, rotation of the axle 966 controls the piston-chamber combination, thereby controlling the pressure in the pistons 968 'and 968 ". From the pressure source 1075 to the control unit 1077 Signal 891. A return channel 1050 having a fluid of reduced pressure (up to the fluid 889) is passed through the cascade pressurization system (translational motion and / or rotary pumps) (see FIG. 12A) And returns to the power supply source 1075.

A flange 1079 connects the chamber 960 with a suspension 1080 mounted on the axle 966. Belt 1081. For example, a pump may be present as reference numeral 821 'and / or 826' in FIG. 13B, but not shown in this view - the pump communicates with the pressure source 1075. The pump will be able to communicate with the axle 966. In addition, the pump will be able to communicate with the flywheel and / or regenerative braking system 1082.

The motors according to FIGS. 12A and 12B may include a chamber 960, at least a portion of which may be parallel to the central axis (not shown) of the chamber.

13A shows a motor as shown in FIG. 11A, wherein the crankshaft arrangement 800 has been replaced by the rotating motor of FIG. 10B.

13B shows the motor of FIG. 13A, wherein piston pumps 818 and 826 have been replaced by rotary pumps, e.g., centrifugal pumps 821 'and 826'.

13C shows the B-B cross-section of Fig. 13B, and the motor is of the type in which the chamber of the actuator piston-chamber combination moves and the piston does not move.

The motor comprises a chamber 860 and the chamber comprises a respective, four sub-chambers 861, 862, 863 and 864, the sub-chambers being connected to one another and around the same central axis 865 Which has an axle 866 through the center 867 of the chamber 860. Inside each of the lower-chambers 861, 862, 863, and 864, there are disposed in each of the lower-rotation chambers 861, 862, 863, and 864 at different angles? Five pistons 868, 869, 870, 871, and 872 are disposed, respectively. Each piston includes a piston rod 873, 874, 875, 876 and 877, respectively. The pistons 868, 869, 870, 871 and 872 are of the "spherical-spherical" type and are shown as having both different diameters. The chamber 860 rotates counterclockwise about the axle 866 and the lower chambers 861, 862, 863, and 864 rotate in a clockwise direction of rotation to a second rotational position and a first rotational position Four holes 878 for assembly of the chamber 860 on the axle 866 are shown.

Fig. 13D shows a cross section taken along line A-A in Fig. 13C. A belt 883 may be mounted to a chamber 860 having a cutout 879 around the flange 861 of the chamber 860. [ A chamber 860 is assembled on the axle 866 having a flange 880 by a recession. The piston rods 873, 874, 875, 876 and 877 are assembled inside the housing 882.

FIG. 13E shows section C-C of FIG. 13A and another cross-section of the housing 882 at A-A. Piston rods 872, 873, 874, 875 and 876 are connected to a pressure distribution center 884 where each piston is connected to a computer 885 steering reduction valve system 886, The signal 887 providing the rotational position of the axle 866 to the computer 885 determines the pressures for each of the pistons by means of the signal 888. [ The pressure for the piston rods 872, 873, 874, 875 and 876 is introduced from the pressure vessel 889 through the channel 890 and is controlled by the signal 891 for the computer 885. The fluctuating pressure changes of both in the enclosed space of each piston are treated independently, but also the adjustment is electronically processed for each piston by the same computer 885. There may be a pump (e.g., the same as reference numerals 821 'and 826' in FIG. 13B), but not shown in this view - the pump communicates with the pressure source 1075. The pump will be able to communicate with the axle 966. In addition, the pump will be able to communicate with the flywheel and / or the regenerative braking system.

Figure 13f schematically illustrates an alternative solution to a motor re-pressurization system, now similar to Figure 11f. Chamber combination 873 communicates the actuator piston 1091 with the piston-chamber combination 873, 872, 874, 876, and 875, while each enclosed space (e.g., 1090) of each piston communicates with the piston- And such a position of the actuator piston in the chamber 1092 is controlled by the position of the cam wheel 1093 so that it can turn over the cam 1094 while the cam 1093 is on the axle 866 Assembled. Note: The cam and the wheel are schematically shown, as each wheel must have a different distance to its associated piston, while the wheel should (partially) be shown in the lateral directions. The pressure inside the enclosed space 1090 is similar to the piston chamber combination 1055 'and other control actuators 1056 (as 1056) and reduction valves 1057' and 1058 ', similar to 1055 from FIG. (Such as 1057, 1058), while being additionally adjustable by a speedometer 841 '(like 841). A pressure vessel 889 communicates with the reduction valves 1057 'and 1058' [1095]. There may be a pump (e.g., the same as reference numerals 821 'and 826' in FIG. 13B), but not shown in this view - the pump communicates with the pressure source 1075. The pump will be able to communicate with the axle 966. In addition, the pump will be able to communicate with the flywheel and / or the regenerative braking system.

13A and 13B may include a chamber 860, at least a portion of which may be parallel to the central axis (not shown) of the chamber.

14A shows an actuator piston 1702 disposed in a chamber 1701 having a central axis 1702 when moving from a second longitudinal / second circular position 1705 to a first longitudinal / A piston 1700, and a piston 1704 mounted on a piston 1702. The piston 1703 has a piston 1702, The actuator piston 1700 is pushed to 3 and 1/2 bar, for example, at the second longitudinal / second circular position 1705. [ The piston 1700 includes an enclosed space 1707, including a pump portion 1708. When moving from the first longitudinal position / first circular position 1706, the second longitudinal / second circular position 1705 to the above-described three and one-half bars until the pressure is reduced to, for example, The pump portion 1708 of the enclosed space 1707 is separated from the rest of the enclosed space 1707 by the piston 1703 when the actuator piston 1700 is depressed - At the first circular position, the actuator piston 1709 now has a significantly larger diameter than the piston at the second longitudinal / second circular position 1705. The piston 1703 is moved to the actuator piston 1709 to retract the actuator piston 1705 to the atmospheric-pressure position 1713, where a return to the second longitudinal position occurs in the case of a crankshaft, The bar overpressure is released in the enclosed space 1707 by retracting (moving 1710) The diameter of the actuator piston 1711 is increased to its production size and its size is reduced to 3 and 1/2 in the wall of the chamber (not shown in this figure) at the second longitudinal position 1705 Which is slightly smaller than the diameter of the actuator piston 1700, which is pressurized to the bar. The piston 1703 may be further retracted from the actuator piston 1711 and moved 1712 so that a pump stroke 1716 toward the second longitudinal position 171 may be generated and the crankshaft In this case, when the actuator piston is returned 1715 toward the first longitudinal position, the actuator piston is pressurized to 3 and 1/2 bar.

Fig. 14b schematically illustrates the process of Fig. 14a in time, and this process includes the addition of a sub-line disposed around a circular, round central axis 1721, - &lt; / RTI &gt; Chamber 1720 generally moves in the direction of arrow 1740 while the actuator piston 1722 is not moved. In this illustration, however, the piston 1720 moves while the sub-chamber is non-moving. The piston 1722 is disposed in the second longitudinal / second circular position and the fluid 1723 in the actuator piston is pressurized to, for example, 3 and 1/2 bar. A pump 1724 includes a piston 1725, a piston rod 1726, a chamber 1727, and a cam wheel 1728. The cam wheel 1728 is placed on the cam surface 1729. The piston 1725 is disposed in the second longitudinal piston 1730 of the pump 1724. When the actuator piston 1722 moves from the second longitudinal / second circular position in the lower-chamber 1720 to the first longitudinal / first circular position, the position of the piston 1725 remains unchanged Where the fluid 1723 is reduced in pressure to 1/2 bar - the actuator piston 1732. As the cam surface 1729 is held at its height, the cam wheel surface 1728 is held in position. Retraction of the piston 1725 from the position 1730 to the position 1731 imparts an internal pressure of zero bar (overpressure) to the actuator piston 1733 and reduces its diameter to its product size. This is the result of the cam surface 1729 being inclined to the cam surface 1734 having an angle a relative to the cam surface 1729 so that the cam wheel 1728 is further away from the actuator piston 1733 The cam wheel 1738 begins to move. Immediately thereafter, the translation of the cam wheel 1738 at the end point 1735 is returned and is returned to the actuator piston 1733, which is further turned to the actuator piston 1736. When the cam wheel 1738 comes back to its original surface 1729 it overrides the inclined cam surface 1739 with an angle beta (&gt; 90 DEG) . The actuator piston 1737 belongs to the position of the cam wheel 1728. It should be emphasized that a reduction in the size of the diameter of the actuator piston can be made progressively for a very short period of time and thus the actuator piston can be kept in contact with the wall 1748 of the chamber 1720. [

Fig. 14C shows the configuration of Fig. 14B to enable fluid injection into the actuator piston when in the second circular position. Cam wheel 1740 now turns over hose 1741 and its chamber 1744 includes wall 1742 and a mixture of fluids or fluids 1743. The hose 1741 is temporarily closed when there is an actuator piston 1747 in a second position (reference numeral 1737 in Figure 14B) that can be re-pressurized from the fluid in the hose 1741, And has an outlet 1745 to the enclosed space 1746 of the actuator piston 1747 which opens only to the enclosed space 1746 of the piston 1747.

The description for FIG. 14d shows conventional (linear cylinder) pumps, which communicate with the enclosed space of actuator pistons, which operate in the same circular chamber. Which has a center axis 1750 in the chamber 1749-wheel 1751-is turned counterclockwise around the axle 1752 mounted with the roll bearings 1753. The chamber includes four identical sub-chambers 1754, 1755, 1756 and 1757. The channel 1750 includes five fixed identical pistons 1758, 1759, 1760, 1761 and 1762, each of which is in a different circular position with respect to each other, and thus with different diameters and internal pressure . Each piston has pump portions 1763, 1764, 1765, 1766 and 1767 and the pump portion is fixed to the center of each of the pistons 1758, 1759, 1760, 1761 and 1762. Each of the pumps has piston rods 1768, 1769, 1770, 1771 and 1772, including cam wheels 1773, 1774, 1775, 1776 and 1777, which operate on camshaft 1778. This camshaft 1778 includes 4x identical lowered portions 1779, 1780, 1781 and 1782, and the pistons 1758, 1759, 1760, 1761 and 1762 need to be repressed, It needs to be pressurized again. The actuator piston 1761 illustrates the use of the lowered portion for the pump with respect to the dashed line 1761 '. Arrow 1783 shows the direction in which the chamber 1749 is turned around the axle 1752.

Except that pump portions (including straight cylinders) 1763, 1764, 1765, 1766 and 1767 are replaced by pump portions (including elongated conical cylinders) 1786, 1787, 1788, 1789 and 1789 , And Fig. 14db is the same as Fig. 14da. A second longitudinal position of the pump portions 1786, 1787, 1788, 1789 and 1790 is disposed closest to the actuator pistons 1791, 1792, 1793, 1794 and 1795. [

Figure 14e shows a section A-A of the motor according to Figure 14db of the present invention, including a circular chamber directly mounted on the wheel of the vehicle. Having a central axis 1901 and a brake pad 1904 mounted by bolts 1955 on the chamber housing 1905 with a circular chamber 1096 therein, Section of the rim 1900 with a suspension of rim on the disk 1902 has a central axis 1907 and the chamber 1906 is shown in cross section wherein a spherical type piston 1908 Lt; RTI ID = 0.0 &gt; 14db. &Lt; / RTI &gt; The interior of the piston 1908 includes an enclosed space 1909 mounted within the housing 1910 which is itself mounted by bolts 1922 on a portion 1911 of the vehicle frame 1912 . The size of the enclosed space 1909 is controlled by a pump 1913 having a conical chamber 1914 and the end of the conical chamber 1914 is actuated on the cam profile 1916 by rollers 1915 do. The cam profile 1916 rotates the cam 1916 around the main motor axle 1918 by roller bearings 1924 and includes the motor (including the circular chamber 1906 and the spherical piston 1908) By an auxiliary electric motor 1917 which independently turns the motor. Roller bearings 1919 for suspension of the chamber 1906 on the main motor axle 1918 and ball bearings 1920 for the cam profile 1916 on the main motor axle 1918 are shown. The main motor axle 1918 is also mounted on the vehicle frame 1912 (not shown) by bolts 1923. The pressure controller 1925 according to the configuration of Fig. 16 ("drive by wire") communicates with a remotely located speedometer 1927 (not shown). The pump 1928 of the pressure controller 1925 communicates with the channel 1926 which contains the enclosed space 1909 of the actuator piston 1908. [ An electric motor 1917 is schematically illustrated as a rotor 1928 secured on an external motor wall 1929, including, for example, a cam 1926. An anchor 1930 is fastened within the main motor axle 1918 so that the anchor 1930 is positioned within the rotor 1928. The chamber housing 1905 is fastened to the main motor axle 1918 by the nut 1931 and the washer 1932. [ The extended axle end 1933 of the roller 1915 of the pump 1913 is guided in the groove parallel to the central axis 1934 of the pump 1913, A translational movement of the second lens group 1914 is generated.

14F shows a cross-sectional view of the circular chamber 1916 shown in Fig. 14E when it is in the first circular position, together with the chamber housing 1905 and the central axis 1907 bolted together by bolts 1955 And an enlarged detail portion. The spherical piston 1908 is shown in cross-section. A wall 1939 of the spherical piston 1908 includes a reinforcing portion (not shown) according to Figures 208e, f or 209a-c and mounted on the closed end 1943 of the piston rod 1942, Located at the end 1940, opposite the end 1941 closest to the pump 1913. The piston rod 1942 has a channel 1944 which communicates with the cavity 1946 of the spherical piston 1908 through the hole 1945. The other end 1941 of the wall 1939 of the spherical piston 1908 is connected to the conical chamber 1914 of the pump 1913 and to the channel 1926 of the pressure controller 1925 (not shown) (1944). End 1941 includes a movable cap 1947 that is sealed on piston rod 1942 by O-ring 1948. A spherical piston 1908 may be mounted (e.g., vulcanized) on the movable cap 1947 and such a movable cap 1047 may slide on the piston rod 1942. To facilitate understanding of this figure, wall 1941 of piston 1908 extends through a cross-section where contact between wall 1941 of piston 1908 and wall 1948 of circular chamber 1916 occurs Not shown. The central axis 1934 of the chamber 1914 of the pump 1913. A piston rod 1942 can translate within the cylinder 1950 and is sealed by two O-rings 1951 and 1952, respectively. The distance aa between the center axis 1953 of the hole 1945 and the center axis 1907 of the circular chamber 1916. The distance cc between the end 1954 of the movable cap 1947 and the center axis 1907.

When the vehicle includes more than one wheel, it may be necessary to synchronize the movement of each wheel with the movement of each other wheel, if the wheels roll on the same surface. This is preferably done by a computer, which controls the pressure in each of the actuator pistons in each lower-chamber per wheel and the pressure in the other wheel. This is illustrated by reference numeral 1960, which communicates with a computer (not shown) 1961.

FIG. 14G shows the same as FIG. 14H, except that the actuator piston 1908 is shown in the second circular position of the chamber 1916. The movable cap 1947 is slid over the piston rod 1942 toward the closed end 1940 and additionally the piston rod 1942 is slid over the cylinder 1950 toward the pressure controller (not shown) Lt; / RTI &gt; The hole 1945 is now disposed between the closed end 1940 and the movable cap 1947. The distance aa (FIG. 14F) is reduced to the distance bb while the distance cc (FIG. 14F) is reduced to the distance dd. Such slides allow the position of the actuator piston 1908 to be adapted at the center of the cross-section of the chamber 1916, at all circular positions of the actuator piston 1908.

14H illustrates the configuration of Fig. 14E wherein a circular chamber housing 1916 is provided between the rim 1900 of the wheel and the brake plate 1902, for example, a built- And a gear box 1956.

14E, it may be necessary to synchronize changes in the gears of the gearboxes 1956, for each one wheel, in addition to the computerized control of the pressure of each actuator piston. This may preferably be done by the computer 1961, which again controls the pressure in the computer, e.g., each actuator piston (Figure 14e).

A description of the updated preferred embodiments from 19622

Figure 14i illustrates a portion of the pressure management system of each of the motors 1970 and 1971 mounted on each of at least two parallelly disposed wheels 1972 and 1973 of the vehicle, for example. Rear wheels 1974 and 1975, respectively. The vehicle turns to the left corner, around the circular center 1976. The left wheel 1972 closest to the center 1976 turns to a smaller radius 1977 than the right wheel 1973 with a radius 1978. [ The left wheel 1972 turns to an angle 'a' and the right wheel turns to an angle b ', where' a '>' b '. As a result, it is necessary that the left wheel should be turning slower than the right wheel, and these signals 1981 and 1982 must be transmitted to the associated motors 1972 and 1973. This is done by sensors 1979 and 1980 which sense the different angles ('a' and 'b'). Each of these signals 1981 and 1982 is passed to and processed by the computer 1983 resulting in each of the control signals 1984 and 1985 so that each of the motors 1970 and 1971 accordingly Change the speed of each.

15a-e illustrate several auxiliary power sources working with the motor. The electrical power lines shown are carefully selected.

15A shows an H ₂ -fuel cell that delivers electricity to a motor driving an ESVT-pump. Today (February 2011), this solution is very expensive, but it has only been conveyed in messages on the Carbon Trust website that there has been a technological breakthrough that will enable the use of H ₂ -fuel cells in vehicle motors in the future. Another difficulty is that the storage of H ₂ is difficult and not energy-friendly.

Figure 15b shows a solution to the H ₂ storage problem because H ₂ is stored as H ₂ O and is free from electrolysis. From studies of feasibility, it has been found that in this way for the generation and use of H ₂ in combustion motors, which can lead to rotation, less than 10% of the current energy is required, for example, to drive the vehicle. The alternator produces electricity, which drives the electric motor to drive the ESVT-pump. The problem here is that the ESVT-pump drive process has only 25% efficiency.

O ₂ liberated from the electrolysis of conductive H ₂ O would be available in the combustion motor, so combustion of H ₂ is still more efficient (turbo-effect). H ₂ O liberated from the combustion process in the combustion motor may be re-used to induce H ₂ by electrolysis.

Figure 15c shows a solution in which the ESVT pump is driven directly by the axle of the combustion motor through the crankshaft, which can now be considerably smaller since the process of supplying power to the pump has 100% efficiency.

15d shows a comparable solution in Fig. 15c, wherein the crankshaft has been replaced by a rotary ESVT-pump, which makes the process still more efficient. H ₂ is obtained from both electrolysis and solar photovoltaics.

15E shows a solution in which a large capacitor is used as a power supply for the ESVT-pumps. It is a great advantage that the vehicle is able to drive 500 km when such a capacitor is charged within a few minutes and the capacitor has the size of the suitcase.

And Figure 15a is a schematic illustration of the storage tank 1630 for O ₂ (1631), such a storage tank for connection will be able to be pressed, and the storage tank 1630 and the external (1633) of the motor channel (1632 ). The storage tank 1630 communicates with the H ₂ fuel cell 1606 through a channel [1634]. Another storage tank 1600 for H ₂ 1601 may be cooled and pressurized using electricity through electrical communication 1602 and the storage tank 1600 may be connected to the exterior 1604 of the motor And is filled through a channel 1603 that is formed by a plurality of channels. The storage tank 1600 communicates with the H ₂ fuel cell 1606 through a channel 1605 where H ₂ and O ₂ are converted to electricity which is supplied to the starter battery 832B ) (Short time, high current) or service battery 832C (long duration, intermediate current). The channel [1605] includes a one-way valve 1708 (not shown). The potential difference required to operate the fuel cell 1606 is established by the electrical communication [1602]. The starter battery 832B is in electrical communication with the starter 830 of the motor while the service battery 832C is in electrical communication with the pump 820/826 of the motor. The motors in which the selected elements are specifically described herein are discussed in detail in Figures 11a, b, g, h, i, j, k, l, k, n and Figures 12a and 13a and 13b. The motor further includes a pressure vessel 814/890 that communicates with the pump 826 and with the piston actuator arrangement 800. The main axle 852 of the motor communicates with the alternator 850 which charges the service battery 832A (long duration, intermediate current) through the electrical communication 1611. [ The battery is in electrical communication with the cooling of the tank 1600. Batteries 832A-C (included) are referred to by reference numeral 832 as one piece in the other figures of the present application and have been charged from the works. The photovoltaic solar cell 833 charges the battery 832 additionally. The pressure storage vessel 814/890 is charged by a pump 820/826. For example, instead of the reduction valve systems 1057 and 1058, as described above in FIG. 11G, the piston actuator module 800 of the motor drives the main axle of the motor 852.

Figure 15b schematically shows a tank 1612 for (conductive) H ₂ O 1613, which tank is connected to the outside of the motor 1629 via a channel 1614 Lt; / RTI &gt; Tank 1612 communicates with vessel 1616 through channel 1615 and electrolytes 1617 of water 1613 within the vessel. An outlet 1622 of the container 1616 communicates with the combustion motor 1620 and the combustion motor communicates with the main axle 1621. The channel [1622] includes a one-way valve 1618 (not shown). The motor 1620 and combusting the H ₂ generated in the container 1616, it moves along - here, the rotation of the axle (1621) is generated. The axle 1621 is in communication with the electric starter motor 1623 and the alternator 1624. Alternator 1624 charges battery 832B (high current, short time) or battery 832C (intermediate current, long duration) for starter motor 1623 through electrical communication line 1619. Battery 832A (medium-high current, long duration) is charged by alternator 850 through electrical communication 1611, which communicates with the motor's main axle 852. The battery 832A provides power through electrical communication [1626] for the electrolysis 1617 in the vessel 1616. The battery 832C provides power through the electrical communication 1627 to the pumps 820/826 of the motor while the battery 832B powers each of the starter motors 1623 and 830 through electrical communication 1628 to provide. Batteries 832 were charged from the jobs. The photovoltaic solar cell 833 charges the battery 832 additionally. The pressure storage vessel 814/890 is charged by a pump 820/826. The piston actuator module (800) of the motor.

15C illustrates a schematic process according to FIG. 15B wherein a piston pump 1625 of a repressurized cascade 820 or 826 is connected to a crankshaft 1636 and a piston rod 1637 via combustion And directly communicates with the main axle 1621 of the motor 1620. In addition to the alternator 850, the photovoltaic solar cell 833 charges the battery 832 in communication with the main axle 852. The battery 832 is electrically connected to the motor 1623 through electrical communication [1628]. The outlet of the pump 1625 of the motor function 820/826 is connected to the motor by a channel 828 and to the pressure storage vessel 814/890, in particular, according to Figures 11a, b, g or 12a, . In this figure, the electrical output 1628 by the battery 832 provides electrical communication for the other functions of the motor, as shown in the previous figures.

15D schematically illustrates the principle of a process comparable to that of FIG. 15C wherein a piston pump 1625 has been replaced by a rotary pump 1635 which is connected to a motor 1620 by an axle 1621 ). The rotary pump 1635 communicates with the pressure storage vessel 814 of Fig. 13B by a channel [828]. The starter motor 1623 communicates with the axle 1621 and acquires power from the battery 832 via the wire 1628. [ The battery 832 is charged by the photovoltaic cells 833 'and the alternator 850 through the wires 1611 and communicates with the axle 1621. The battery 832 is connected to the motor functions 800 by a wire [1627]. Photovoltaic cells 833 'provide H ₂ directly to motor 1620 by channel [1640]. Such a system would preferably be used in conjunction with the arrangements shown in Figures 13f, 14b, c, and d. The motor type according to Fig. 14d may be a particularly preferred embodiment. In this figure, the electrical output 1628 by the battery 832 provides electrical communication for other functions of the motor, shown in the preceding figures.

Figure 15e schematically illustrates a capacitor 1641 for instant storage of electricity 1642 filled through an electrical wire 1643 that connects a capacitor 1641 to the exterior 1644 of the motor. The capacitor 1641 communicates through channel 1645 to the other functions of the motor in the figures according to function 851 of Figures 11a, b, c, f, g and Figures 12a and 13a, b. The functions include axles 852, 866, and 1621, respectively, in communication with alternator 850 or 1624. The battery 832 is electrically connected to the alternator 850 (not shown in FIG. 15E) by wires 1611. The battery 832 is additionally charged by the photovoltaic solar cell 833. Additionally, capacitor 1630 is connected to battery 832 by wire [1646] for charging purposes.

Fig. 16A shows an enlarged view of the 2-way actuator of Fig. 11G-r. The two-way actuator is in communication with each of the regulators (reduction valves) 3303 and 3304 controlled by the speedometer 3306 via the valve means 3305, respectively - the regulators 3303 and 3304 are in communication with each other And two channels 3300 and 3301 communicating internally from the outside of the cylinder 3302 so that a single speedometer 3306 can control both regulators 3303 and 3304. There are two overflow channels 3307 and 3308 in communication with each of the two spaces 3309 and 3310 on each side of the inner piston 3311. O-rings 3312 and 3313 are present between the piston 331 and the wall 3314 of the actuator.

Figure 16b shows a pre-study of the two-way actuator of Figure 16a. It has been concluded that a system that responds more quickly is a piston that includes overflow channels. Additionally, it has been concluded that regulators need to have each of the stop functions for that flow. And, it is necessary that the overflow channels have (1) an automatic reverse valve function (for example, according to FIG. 210E) and (2) a check valve, respectively.

ESVT - asynchronous crankshaft design - combined use of components

17A shows a complete cycle of an actuator piston in a conical chamber using ESVT. This is the same as Figs. 10a-c. Although only an elliptical-elliptical / spherical type piston is shown, any type of expandable actuator piston may be used.

Figures 17b-h show a multiple cylinder motor based on the two-cylinder configuration of Figure 17b. Fig. 17B is based on one cylinder configuration of Fig. 17A, where the configuration is shown in a manner such that the power stroke of one chamber and the return stroke of the other chamber (not powered) Respectively. Since the power stroke of the actuator piston is effected only from the second longitudinal position to the first longitudinal position, the two chambers are pointing in opposite directions. As a result, the crankshaft configuration is such that the connecting rods for these actuator pistons are arranged at 180 [deg.] With respect to each other ('asynchronous'). As a result, the motor delivers power at all times, and such a configuration could be used in a stand alone two-cylinder motor, or in a plurality (> 2, preferably even) cylinder motors. The flywheel can be extraordinary and the omission of such a flywheel will reduce the weight of the vehicle.

Both actuator pistons may or may not communicate with each other through enclosed spaces of a crankshaft (each of which may include two connected lower-crankshafts, one for the actuator piston), each belonging to a different actuator piston There will be. Communication between the enclosed spaces may be through channels in the sub-crankshafts and / or through channels outside the crankshaft.

The enclosed spaces may be arranged, for example, at the connection points of the lower-crankshafts (together with the crankshaft), between the enclosed spaces, for example, a tightening rod 1270 ) (Fig. 11x).

In this configuration of actuator pistons, as each pressure increase and decrease for each actuator piston is reversed at the same time, the total volume of enclosed spaces can be maintained, so that the two ESVT pumps It would be quite easy to combine with a pump. The ESVT-pump, for example, communicates directly with one of the enclosed spaces, while the ESVT-pump indirectly communicates with the other enclosed space through the outer channel.

To the respective enclosed space for each actuator piston (e.g., by use of valve actuators according to Figures 210e or 210f) to open and close the connection between the ESVT-pump and the enclosed spaces, There may be valves that function in both flow directions, from the space. The valves are connected by tappets that can communicate with or communicate with a computer (not shown) with a camshaft (which may be in communication with a main auxiliary power line, e.g., a secondary H ₂ combustion motor) And / or the pressure of the ESVT-pump.

When the actuator pistons are in the first / second longitudinal positions and in the second / first longitudinal positions, respectively, the pressure inside the actuator pistons changes. When the camshaft is able to regulate the opening and closing of the actuator piston + check valve assemblies, the camshaft will be able to double the speed of the axle, where the crankshaft of the ESVT-pump communicates.

Piston-chamber combinations for each of the enclosed spaces in the lower-crankshaft, which change the speed / pressure in the cylinder, may be used for only one cylinder. These piston-chamber combinations communicate with each other through the electrical pressure regulator of the two-way actuators, which move the respective piston rod of the piston-chamber combinations and thereby communicate with an external speedometer. However, one of the two piston-chamber combinations may be eliminated and replaced by the same configuration used to cut one of the ESVT-pumps, whereby the settings of the piston- . Many valves may make such a configuration vulnerable to malfunctions.

Instead of the toothed belts at the power side of the auxiliary motor, it will be very easy to replace them by the gear wheels where the pump (s) is driven.

When the second and third enclosed spaces are able to communicate with each other, for example, at the connection points of the sub-crankshafts (Figure 11w, w '), for example, the movable piston (Figure 17i) , This could be mounted in a channel containing the enclosed spaces. The piston is of a dual function type such that when the piston is moved toward, for example, the second enclosed space, thereby increasing the pressure in the second enclosed space of one of the actuator pistons, the other actuator piston The pressure in the third enclosed space is simultaneously reduced. The double working piston is essentially an ESVT-pump of the corresponding configuration of the motor. Additionally, the dual working piston may be disposed outside the crankshaft.

Wherein the motor further comprises two cylinders in which the second longitudinal position of one cylinder is at the same geometrical level of the first longitudinal position of the second cylinder and both actuator pistons communicate with each other through the crankshaft And the crankshaft includes two connected sub-crankshafts, one for each actuator piston, and the connecting rods for these actuator pistons are disposed at 180 DEG from each other.

Wherein the motor further comprises ESVT pumps for each of the cylinders, wherein through the sealed space of one of the actuator pistons and the communication of the enclosed space of the other of the actuator pistons, the pumps are connected to the two cylinders And the enclosed spaces are contained in the crankshaft, and the enclosed spaces communicate with each other at connection points of the lower-crankshafts.

Wherein the motor further comprises valves, the valves opening and closing the connection between the ESVT-pump and the second or third enclosed spaces, each connection having a check valve or check valve function, Are controlled by the pressure of the ESVT-pump and / or by the tappets, which communicate with the crankshaft in communication with the main axle of the auxiliary motor.

The motor further comprises more than two cylinders, wherein each additional cylinder communicates through the enclosed spaces of the connected lower-crankshafts of the existing sub-crankshafts.

In Fig. 17i, a two-cylinder motor is disclosed in which the enclosed spaces of each chamber in each lower-crankshaft are defined by a linear channel in which the two-way piston moves in and communicates with the respective enclosed space .

17A, an elliptical / elliptical-spherical actuator piston 217 is shown in a first longitudinal position. The actuator piston is inflatable and is operated in a chamber having different cross-sectional areas at first and second longitudinal positions. The cross-sectional area and the circumferential length in the second longitudinal direction are smaller than the cross-sectional area and the circumferential length at the first longitudinal position. When the first longitudinal position is reached, the actuator piston is the final position of the power stroke. During power stroke, the actuator piston moves from the first longitudinal position to the first longitudinal position under the influence of the pressurized fluid inside the piston container.

The enclosed space that allows the fluid in the piston container to be in a continuous, open communication remains the same during the power stroke. The enclosed space of the piston actuator communicates with the channel and controls the volume of the space enclosed by the valve within the channel. During a power stroke, the valve is positioned closest to the actuator piston.

During the movement from the second longitudinal position to the first longitudinal position, the pressurized elliptical piston 217 'is inflated with the spherical piston 217, and with the expansion of the piston container, . At the first longitudinal position, the fluid inside the piston is still a little overpressure, thereby ensuring a good seal to the chamber walls. The piston 217 may also be elliptical in shape.

When the position of the valve is maintained unchanged during the power stroke, the valve is retracted further away from the actuator piston. The volume of the enclosed space is increased and the internal pressure is reduced to the pressure at which the piston was produced. The fluid in the enclosed space and the piston container continue to communicate openly with each other. Thereby, when there is a pressure difference between the fluid in the piston container and the enclosed space, a new equilibrium will be established. In Fig. 17A, the valve moves from level "0" to "1 ". During the return stroke, the actuator piston assembly is relocated to the second longitudinal position and the volume of the enclosed space is reduced to a value of &lt; RTI ID = 0.0 &gt; When the piston is moved from the first longitudinal position to the second longitudinal position, the piston is depressurized and is free from the wall or is merely engaged, but from the volume below the piston, It will not seal the upper volume. The returned piston 217 "'is now held by the wall of the conical chamber and retains its shape when pressed against the piston 217'. Pressurization is realized by changing the position of the valve in the channel in which the enclosed space communicates. By reducing the volume of the enclosed space with increased pressure, the valve extends from level "1" to "0 ". The pressurized piston will move again from the second longitudinal position to the first longitudinal position, completing one overall cycle. The piston expands to the initial piston shape 217 to reduce the internal pressure. Movement is driven by the high pressure in the piston and the force exerted on the walls of the chamber due to the reaction force provided in response to the actuator piston.

This is referred to as the power stroke as the main axle to which the actuator pistons are connected / attached receives energy from mechanical movement. Following the valve in the channel, various configurations can manage pressures and depressurisations of the actuator pistons.

A two-cylinder configuration is shown in Figure 17B. The two cylinders are the same as in Fig. 17A, except that the internal orientation is 180 deg. For example, when the actuator piston in the cylinder assembly A is at the start of the power stroke, the actuator piston of the cylinder assembly B is at the start of the return stroke. 17B, it is shown rotating the cylinder configuration by 180 degrees, but in the motor, for example, the cylinders are arranged in parallel and the cylinder B over one 180 degrees to one of the cylinder assemblies A, By rotating the crankshaft connection to the crankshaft, there are several possibilities to realize this. The cylinder pressure systems may communicate with each other or may have their own support systems. The main crankshaft of the motor includes two sub-crankshafts, one for each cylinder-piston assembly. The cycle of the actuator piston in the conical chamber is described in the description of Figure 17 and the installation of the cylinders and the processes in the motor are handled in Figures 17c-h.

17C-17H, a process description of one complete cycle of a motor configuration consisting of two cylinders is given. The disclosed two-cylinder motor configuration consists of one main axle comprising two sub-crankshafts wherein the enclosed spaces of each chamber in each lower-crankshaft are separated by a tightening rod 1270 . When the cylinders are operating asynchronously (180 degrees difference) and accordingly one cylinder starts the power stroke, the other cylinder is at the beginning of the return stroke, which is similar to that shown in FIG. 17B.

Within the motor, one ESVT pump is replaced by an inflow / outflow connector, which is connected to the remaining ESVT pump. By means of valves 459/423 and 462/422, the flow for pressurizing and depressurizing both pistons is controlled. For each cylinder, one set of valves is installed in accordance with the concepts of Figures 210e and 210f, and thus one is installed for the inflow flow of fluid and one for the outflow flow. The valves are controlled by tappets and pressure in communication with the cams on the camshaft.

Both crankshafts of the ESVT pump and the camshaft are driven by the H ₂ combustion engine through the gear wheels and the toothed wheel-belt arrangement, enabling various speed (pre) settings. 17C-h, the rotational speeds of the camshaft, the pump-crankshaft, and the main axle are the same.

The remaining ESVT pumps are of special type, where the volume of the upper piston is connected to one cylinder assembly and the volume below the piston is connected to a different cylinder assembly. Since the cylinders operate asynchronously, this arrangement allows for the desired pressure scheme, i. E. For piston actuators requiring reduced pressure, low pressure and pressure on one side of the ESVT pump piston are required to provide high pressure for the piston actuator. An ESVT pump 8000 with a special configuration can be used for additional motor configurations and is applicable, for example, in Figures 17c-17h.

For each set of valves, there is a cam installed on the camshaft. Each cam provides two different signals during one revolution, one for the inlet flow valve and another for the outlet flow valve. The cams of each valve set are equally installed on the camshaft so that when the first signal is provided by the first cam the second cam also provides the first signal and the positive The cams provide a second signal. Because the cylinders operate asynchronously, when a first signal from the first cam is used for the inlet flow valve, a second signal from the second cam is used for the outlet valve of the other cylinder assembly, and the second signal The opposite is true. Different configurations of the cams are also possible, as long as they can lead to the desired function of the valves.

The valves are of a special type, as shown in Figure 211 ea. Only when the valve piston is closed and there is an overpressure in the direction of the valve actuator, flow is possible. The overpressure is related to the preset flow strength of the valve by the exhaust flow chamber plus the spring force supporting the piston core. A channel in the valve communicates with the inlet flow chamber of the valve. By the same pressure in the inlet flow chamber and the valve channel, the valve actuator is held in place and thus held in the closed position. When the valve piston receives and closes the signal by an appropriate cam, communication between the valve channel and the inlet flow chamber is blocked. When an overpressure occurs in this setting, the valve is opened. At the moment the valve piston is closed, not only does it block the communication line with the inlet flow chamber of the valve channel, but also opens the channel for communication from the valve channel to the outlet flow chamber. The pressure in the valve channel is switched from the pressure of the inlet flow chamber to the pressure of the outlet flow chamber at the time of closing of the valve piston. Since the pressure in the valve channel is balanced with the outflow flow chamber, it does not need to be overcome. Upon removal of the signal from the valve piston by the cam, the valve actuator is returned to its closed position, communication to the inlet flow channel by the valve channel is re-established and communication to the outlet flow chamber is blocked.

For the inflow valve of the valve set, which controls the pressurization of the actuator, an ESVT pump is located on the inlet flow channel side and a piston actuator with the enclosed space is located on the outlet flow chamber side. For a flow-through valve, this is the opposite. The valve piston is closed by the cam signal, and such cam signal becomes only once for every rotation of the camshaft. During such closing of the valve piston, when the pressure difference across the valve is positive, fluid flow into and out of the cylinder is possible.

Further, the motor is based on the configuration of Fig. 11r and the auxiliary power source, and the H ₂ combustion engine follows Fig. 15d.

17C, cylinder 800L is in the second longitudinal position and cylinder 800R is in the first longitudinal position. The ESVT pump reduces the upper end volume in the cylinder and pressurizes the fluid in the channels of the cylinder assembly including 800L. By reducing the top volume, the ESVT pump increases the bottom volume and thereby lowers the pressure in the 800R cylinder system. The camshaft provides a signal to the inlet flow valve of the channel in communication with the cylinder 800L. The valve position is closed and the pressure in the channel of the valve equilibrates to the pressure in the enclosed space associated with the 800 L actuator piston. The pressure from the ESVT pump accumulates and becomes larger as the pressure in the sealed space communicates directly with the cylinder 800L and opens. By overpressure, the valve actuator pushes the core pin to one side and the fluid can flow in the direction of the cylinder 800L, pressurizing the piston and preparing the piston for power stroke. The outlet flow valve of 800L does not receive any signal, thereby opening the valve piston and not allowing flow.

The camshaft has a second cam, which also provides a first signal, for the cylinder assembly 800R. As the cylinders operate asynchronously, this first signal from the second cam communicates with the outflow valve of the 800R. The valve piston of the outflow valve of the piston 800R is closed, thereby allowing flow from the actuator piston to the ESVT pump. The inlet flow valve of the 800R does not receive a signal, and therefore the flow of fluid towards the actuator piston is not possible. At the moment of FIG. 17C, the piston actuator of 800R is located at the first longitudinal position, at the beginning of the power stroke end and the return stroke. The piston container still has a small overpressure, thereby ensuring good sealing and contact with the wall. The lower end of the ESVT pump has an increased volume and is thereby reduced to a lower pressure. By closing the valve piston, the communication of the valve channel is switched from the actuator piston and the associated enclosed space to the ESVT pump. Due to the overall pressure situation, there is an overpressure from the actuator piston and the associated enclosed space to the ESVT pump. Flow will be initiated from the piston and enclosed space toward the ESVT pump until the pressure at both sides of the valve is balanced (ignoring the small force of the spring supporting the core pin) Will be opened again and will continue until communication is interrupted.

Figure 17ca shows an enlarged view of the left part of Figure 17c.

Fig. 17cb shows an enlarged view of the right part of Fig. 17c.

17D, the motor system axles were further rotated by 1/6 of one revolution. In Figure 17c, the ESVT pump reduced the upper end volume of the piston, and in Figure 17d the piston stopped in place, where the upper end volume was smaller and the lower volume was larger. By the rotation of the crankshaft, the fluid on the piston is slightly more compressed, and the bottom is further expanded. The pressurization by the ESVT pump may also be divided into a top half with a high pressure and a bottom half with a low pressure whereby a shift from one side to the other is important and represents a change with the previous situation. This division into the upper and lower halves applies to the cylinder assembly 800L, and the situation is reversed for the cylinder assembly 800R. After the crankshaft determines the volumes in the ESVT pump, the camshaft is also rotated. In this new situation, the cams do not provide input signals to any of the valves. As a result, the valve pistons are open and no flow is possible to or from the actuator piston and the enclosed space. The resultant reactive force of the wall applied to the piston causes the pressurized piston in the cylinder assembly 800L to move from the second longitudinal position to the first longitudinal position. During upward movement, the piston expands under the influence of the pressure inside the piston to maintain good sealing and contact with the wall of the chamber. The piston of assembly 800R is depressurized and moves downward or downward without contact with the wall to simply engage the wall.

Fig. 17d shows an enlarged view of the left part of Fig. 17d.

Figure 17db shows an enlarged view of the right portion of Figure 17d.

17E, the piston of the cylinder assembly 800L reaches the end of the power stroke at the first longitudinal position. The actuator piston of the cylinder assembly 800R is still depressurized and reaches the end of the return stroke at the second longitudinal position. The various shafts are rotated by an additional 60 degrees. The 800 L piston is fully expanded into the chamber and still under a slight overpressure to ensure good sealing of the walls. The pressure inside the piston of 800 L, and thus the pressure in the channel communicating with the 800 L piston, is the lowest value of the power stroke at the highest position in the chamber (or at the first longitudinal position). The camshaft does not provide a signal to the valves, thereby opening the valve pistons and not allowing inlet or outlet flow. The ESVT pump driven by the connector with respect to the crankshaft is still oriented so that the volume of the upper end of the piston of the ESVT pump is minimized and consequently results in a high pressure and the volume of the lower portion of the piston is maintained at a low pressure. do.

During the first half of the process in Figures 17C-17E, the piston actuator of the cylinder 800L has undergone a power stroke, thereby providing power to the main axle. The main axle rotates at the same speed as the crankshaft and the camshaft. Only the piston actuator of 800R translates from the first longitudinal position to the second longitudinal position, using minimal work. This necessary work is provided by the main axle. Other components that require energy are powered by an auxiliary power source, e.g., a crankshaft and a camshaft.

17E shows an enlarged view of the left portion of FIG. 17E.

Figure 17eb shows an enlarged view of the right portion of Figure 17e.

In Fig. 17F, the cams on the camshaft again provide a signal. The camshaft is additionally rotated and here rotated by more than 180 degrees for the starting situation of Figure 17c. Also, the signal by the cam is different from what is effective in Fig. 17C. The signal closes the valve piston of the outflow valve of cylinder 800L. At the end of the power stroke, the pressure in the valve channel is equal to some overpressure in the piston actuator. With the valve piston closed, the valve channel exchanges fluid with the ESVT pump to balance the two pressures. The ESVT pump piston makes a stroke to enlarge the upper end volume of the piston and consequently reduces the pressure in that space. A slight overpressure of the piston actuator 800L has a positive pressure differential greater than the pressure of the valve outlet flow chamber and is equal to the pressure at the upper end of the ESVT pump. A positive pressure differential will move the valve actuator, push the core pin to one side, and allow fluid from the actuator piston to move towards the ESVT pump. This reduces the pressure of the piston and prepares the piston for the return stroke, and the piston must be free from the wall in the return stroke or simply coupled. As the valve piston of the 800L inlet flow valve does not receive a signal by the cam, it keeps the cam open and prevents flow through the valve.

In the case of a valve set controlling the pressurization of the piston of the piston 800R and associated enclosed spaces, the signal by the second cam closes the valve piston of the inlet flow valve. The valve piston of the outflow valve is kept open and thus does not promote the flow from the piston to the ESVT pump. With the valve piston of the inlet flow valve closed, the pressure of the valve channel communicates with the internal volume of the depressurized piston, so that the return stroke for the second longitudinal position is terminated. As the ESVT pump makes the stroke and as the volume of the piston bottom of the ESVT pump decreases, the fluid in this volume is pressurized. The pressurized fluid in the ESVT pump used when the cylinder assembly 800R communicates results in a positive pressure differential across the valve actuator. This pressure differential allows flow from the ESVT pump to the actuator piston and associated enclosed spaces. As a result of the piston container being under pressure and requiring expansion, the piston container, instead, applies a force on the walls as the outside of the piston is held by the walls of the conical chamber, &Lt; / RTI &gt; This reaction force has components along the length of the chamber and drives the piston. Accordingly, by pressing the piston of the 800R, it is possible to perform an approaching power stroke.

In Fig. 17F, the situation of the cylinder assemblies 800L and 800R is the situation of the other cylinder assemblies in the half cycle before Fig. 17C. The pressures, valve settings, longitudinal positions, etc. are comparable to those in Fig. 17c for another piston to have smooth motor operation.

Figure 17fa shows an enlarged view of the left part of Figure 17f.

Fig. 17fb shows an enlarged view of the right part of Fig. 17f.

In Figs. 17G and 17H, the axles rotate by 1/6 rotation each, completing the cycle. Cams on the camshaft do not provide a signal in these two steps. As a result, the valve pistons of the inlet flow and outlet flow valves of both valve sets are kept open. As the valve pistons are opened, the pressures pushing the actuator valves from the inlet flow chambers of each valve are counteracted by the pressure of the valve channel, which always communicates with the inlet flow chamber of the valve. As the valve actuators are held in place, no flow occurs between the ESVT pump and the piston actuators.

Also, the setting of the ESVT pump can be compared to the setting of Figure 17f. The volume on the piston in the ESVT pump is largely maintained, resulting in low pressure in the top fluid, which communicates with the cylinder assembly 800L. And, the volume under the piston, which communicates with the cylinder assembly 800R, is kept small, resulting in high pressure. In the absence of fluid flow in Figures 17g, h, there is no additional result, but again for the transition from Figure 17h to Figure 17c, the piston in the ESVT pump, which is important in generating positive pressure differences for the appropriate valves The pressure is changed by the return stroke.

17G, piston assembly 800L moves from a first longitudinal position to a second longitudinal position. The piston moves from the first longitudinal position to the second longitudinal position. The piston is in an unpressurized state and is free of the walls of the chamber, or merely engages the walls. At the same time, the cylinder assembly 800R performs a power stroke from the second longitudinal position to the first longitudinal position. Thereby, the pressurized piston expands, lowering the internal pressure and maintaining good contact with the walls of the conical chamber.

17H, the piston actuator of assembly 800L finishes the return stroke and reaches the small end of the conical chamber, where the cross-sectional area and circumferential length are the smallest. The pressurized actuator piston of the cylinder assembly 800R reaches a first longitudinal position where the piston is inflated to a maximum within the large end of the conical chamber where the greatest cross sectional area and circumferential length are greatest. A slight overpressure is maintained in the piston to ensure a good seal against the walls until the final movement of the power stroke. At this point, the normal direction of the walls is perpendicular or nearly perpendicular to the longitudinal axis of the chamber.

Figure 17ga shows an enlarged view of the left part of Figure 17g.

Fig. 17gb shows an enlarged view of the right part of Fig. 17g.

Fig. 17H shows an enlarged view of the left part of Fig. 17H.

Figure 17hb shows an enlarged view of the right part of Figure 17h.

The next step in the continued operation of the motor is again shown in Figure 17c. Thus, this cycle of the six intermediate stages of Figures 17c-h illustrates a complete cycle of the motor including two cylinders operating asynchronously.

Figure 17i shows an example of how the ESVT pump is seen when installed in the connection of two lower-crankshafts. The motor elements are the same as the motor shown in Figs. 17C-17H. The ESVT pump may be operated by a mechanism internal to the cylinder, which is in line with the axis of the crankshaft, for example by a worm wheel or an installation by springs. The piston inside the linear channel forming the ESVT pump may also be driven by an external system. Way pistons move within the chamber thereby enlarging the volume of the enclosed space moving away and reducing the volume of the enclosed space moving closer to the chamber. This reduces and increases the pressure within the enclosed spaces, respectively. The piston seals both enclosed areas at the same time.

ESVT - synchronous crankshaft design - combined use of components

Figures 18a-g (inclusive) refer to a two-cylinder configuration based on the two-cylinder configuration of Figure 18a, based on one cylinder configuration of Figure 17a, with reference to Figures 10a, Cylinder motors. However, any type of inflatable actuator piston may be used.

18A shows two embodiments that are concurrently combined with the power stroke time of each cylinder. Both actuator pistons communicate with each other through a crankshaft (which may include two sub-crankshafts), wherein the connecting rods for these actuator pistons are disposed at 0 [deg.] From each other.

This is done by the construction of two identical piston-chamber combinations, wherein the second longitudinal position of one cylinder is at the same geometrical level as the second longitudinal position of the second cylinder. Accordingly, such a configuration may be combined with other configurations (motors including more than two cylinders) so as not to be powered into the return stroke and to fill the power gap in the return stroke. The use of a flywheel may be another solution.

For example, at the connection point of the sub-crankshafts, through connecting the enclosed spaces of the actuator pistons, ESVT pumps could be combined into one pump for the two cylinders to be one pump.

If another group of actuator pistons is added to the motor, and if the strokes of the added piston-chamber combinations are the same as the strokes of the motor, then the arrangement of FIG. 18 could be used for the entire group- ESVT-pumps of the present invention may be used for a single piston-chamber combination as well as for a full group of piston-chamber combinations for pressure / speed control.

If the other group of actuator pistons is added to the motor and the strokes of the added piston-chamber combinations are opposite to the strokes of the motor, then the configuration of Fig. 17 can be used for the whole group - one ESVT - The pump may be used for the entire group of piston-chamber combinations combined with one-way valves and valve actuators along the outer channel, and both flow directions (Figures 17c-17h (inclusive)). The two crankshafts of both groups of piston-chamber combinations will be able to communicate with each other so that the channels within each crankshaft are preferably communicated, for example, with fillers (e. G., Tightening rod 1270 )). &Lt; / RTI &gt; Power balances may be generated in the motor, thereby configuring the power strokes of the various actuator pistons so that the motor provides a constant power.

In Figures 18b-18g, the pressurization scheme of the motor in one cycle is disclosed. The motor has two cylinder configurations as shown in Fig. 18A. The piston actuators of each cylinder assembly become continuous at the same stage in the cycle, and the piston actuators operate in parallel.

The motor is based on Fig. 11r, and the motors in Figs. 17c-17h are based on this concept, the main difference being the piston pressurization. The auxiliary power source is a forced liquid cooled, H ₂ combustion engine. An auxiliary power source provides work for pumps, batteries, and crankshafts.

Two piston actuators mounted on the crankshaft are connected to one ESVT pump. As the pressure system of both pistons is the same, the pressure settings required from the ESVT pumps by the pistons actuators are the same. This would allow the two ESVT pumps for each actuator piston to be simply and independently connected to a single, shared ESVT pump 1055, only the size of which could be adapted. Following the ESVT pump, one piston chamber combination 1050 is also installed for pressure / speed control in this two-cylinder configuration. The communication between the two actuator pistons occurs at the connection of the two lower-crankshafts, where the second and third enclosed spaces are connected as shown in Figure 11w or w '.

No valves are installed between the ESVT pump and the enclosed spaces or assemblies 800L and 800R. To disengage the connection between the ESVT pumps and the actuator piston, the connector may be configured to enable fluid flow to or from the ESVT pump, or to prevent such communication and to reduce the amount of fluid in the enclosed space and the associated piston Quot ;, and &quot; holes &quot; An example of a connection between an actuator piston assembly and a crankshaft in an enclosed space is shown in Figure 11t.

In Fig. 18B, the communication lines from the enclosed spaces in the lower-crankshafts to the associated piston actuator are opened to permit fluid flow. The actuator pistons have just completed the return stroke and are in the second longitudinal position. The crankshaft of the ESVT pump creates an upward stroke, reducing the volume inside the chamber and raising the pressure of the fluid in the ESVT pump. With the communication line to the actuator pistons open, the pressurized fluid can flow into the reduced pressure actuator pistons. During the return stroke, the actuator pressure is reduced to not contact the walls or merely engage the walls, and does not seal the volume in the chamber below the piston from the upper volume. And with the pressure in the ESVT pump being higher than the pressure in the piston actuator, high pressure fluid flows into the piston actuator. The pressurization of the actuator pistons establishes good contact with the chamber walls and the overpressure tends to cause the piston actuator to expand and such expansion is blocked by the chamber wall or the piston actuator toward the first longitudinal position due to the conical shape of the reaction force. .

18B shows an enlarged view of the left part of FIG. 18B.

Fig. 18Bb shows an enlarged view of the right part of Fig. 18B.

In Fig. 18C, the piston actuators are in the middle of the power stroke of the motor, and the crankshaft of the motor rotates upward. Since the piston actuators move synchronously, the situation for both cylinder assemblies is the same. The crankshaft of the motor is slightly rotated to close the communication line between the piston actuator and the enclosed space in the sub-crankshaft, which is constant and opens communication with the ESVT pump. By overpressure, the pistons are expanded to an enlarged area of the conical chamber. As there is no communication with the ESVT pump and the internal volume is increased, the internal pressure of the piston is reduced. The ESVT pump maintains a small volume within the chamber, maintaining high pressure within the connected systems.

Figure 18ca shows an enlarged view of the left part of Figure 18c.

Fig. 18cb shows an enlarged view of the right part of Fig. 18c.

In Fig. 18D, the piston actuators reach the end of the power stroke. The pistons were expanded to the maximum within the conical shaped chamber. The pistons moved to a first longitudinal position in the chamber. Although the volume in the actuator piston has increased, the fluid inside the piston is under overpressure and thus establishes good contact with the chamber walls for the entire power stroke. The crankshaft of the motor to which the pistons are connected is anti-rotated with respect to the starting situation of Fig. As the holes in the connector from the piston rod to the enclosed space in the lower-crankshaft are closed and consequently the enclosed spaces of the lower-crankshaft are connected, communication between the piston actuator fluid and the ESVT pump, or other piston actuator, Does not exist. The amount of fluid in the piston remains the same. The fluid in the ESVT pump is pressurized by the small volume in the chamber.

Fig. 18d shows an enlarged view of the left part of Fig. 18d.

18d shows an enlarged view of the right part of FIG. 18d.

In Figure 18e, the crankshaft of the motor has been slightly further turned, thereby opening the holes between the enclosed space in the crankshaft and the piston rod and allowing fluid flow. The crankshaft of the ESVT pump has made a stroke so that the connected piston in the ESVT pump is moved away from the outflow flow of the pump chamber and the volume in the ESVT pump is expanded and the pressure is reduced. The reduced pressure in the ESVT pump is less than some depressurization in the piston and consequently the fluid from the piston will flow outward in the direction of the ESVT pump thereby depressurizing the piston. By losing the internal pressure, the shape of the piston is changed from a spherical-elliptical shape in contact with the walls at the first longitudinal position, to an elliptical shape free from or simply coupled to the wall. In addition, the piston may have a different configuration with a contouring system that may be different from this. The piston actuators of both cylinder assemblies 800L and 800R are located at the start of the return stroke.

Fig. 18ea shows an enlarged view of the left part of Fig. 18e.

Figure 18eb shows an enlarged view of the right portion of Figure 18e.

18F, the actuator pistons 800L and 800R are in the middle of the return stroke. The crankshaft of the motor is moved downward to provide an operation for moving the depressurized cylinders from the first longitudinal position to the second longitudinal position. As the communication in the connector is again interrupted, the actuator pistons are kept depressurized. The pressure is also constant as the amount of fluid in the piston systems remains the same and the volume remains the same. The piston maintains the shape it has at the end of the stage shown in Figure 18e. The volume of the chamber in the ESVT pump is kept large, so that the fluid in the piston flows in the direction of the ESVT pump until the closing of the communication with the piston.

Figure 18fa shows an enlarged view of the left part of Figure 18f.

Fig. 18fb shows an enlarged view of the right part of Fig. 18f.

In Figure 18g, the piston actuators complete the cycle and reach a second longitudinal position. The ESVT pump again slightly reduces the volume within the chamber, but the pressure remains low. In addition, the holes for communication between the ESVT pump and the actuator piston are closed. During a power stroke, the piston actuators work on the crankshaft to power the connected systems, while the crankshaft provides a work for moving the piston actuators during the return stroke of both piston actuators, The power supply is not continuous.

Figure 18ga shows an enlarged view of the left part of Figure 18g.

18gb shows an enlarged view of the right part of Fig. 18g.

CT - crankshaft design - combined use of components

Figure 19a is, on the basis of FIG. 11b, 11c, on the one here shown a cylinder motor, and has portions are further configured - the auxiliary power supply, for example, was selected as a combustion motor, such a combustion motor are H ₂ And burns H ₂ derived from the electrolysis of O. The water storage vessel 1612 can be filled with H ₂ O 1613 through the filler opening 1614 by an external source. H ₂ O can be transferred from the water reservoir to the vessel 1616 by way of the channel [1615]. The power needed to implement the electrolytes 1617 in the vessel is provided by a communication line 1069 that contacts the battery 832. The battery 832 can be charged by the solar cells 833 and receives energy by the alternator 850. The alternator is in communication with the main crankshaft 852 of the motor by a toothed belt and gear wheels. The battery will be able to provide a signal to the electrical starter motor 830. Other communication lines from the battery may provide input to the reducing valve 840 and such input may be provided from the pressure storage vessel 814 to the second enclosure of the piston cylinder assembly 800L through the channel 829. [ To control the flow of fluid to the inlet flow connector of the space. The setting of the check valve 840 is controlled by a speedometer 841. The output of the electrolysis process, H _2, is supplied to the combustion engine 3525 by a channel [3545]. Alternatively, O ₂ is transferred to the combustion engine 3525 by a separate channel [3546]. In the engine, under the control of the signal by the communication line 1069, H ₂ and O ₂ are processed to produce water, which is supplied to the water storage vessel 1612 in a return (not shown) . The combustion engine can also generate heat, which will be able to be conducted away by the heat exchanger and be used for secondary use outside of such a motor. The combustion engine provides power to the shaft to which the piston pump 826 is connected. The piston pump presses the fluid introduced by the channel [825] from the outlet flow connector on the crankshaft, which is connected to the third enclosed space of the cylinder assembly. The free end of the crankshaft 852 may be connected to a flywheel 835, a clutch 836, or a gear wheel 837 (not shown).

The piston assembly 800L operates in accordance with the consuming technique as shown in Fig. 11A. The fluid in the second enclosed space in the crankshaft becomes pressure in the pressure reservoir 814 or reduced pressure after passage by the reducing valve 840 while the channel 825 connected to the outlet flow connector is at a low pressure But such pressure may be varied by a one-way valve at the end of the channel that controls a positive pressure differential with respect to the pressure of the piston pump 826. [ The piston actuator is connected to the crankshaft by the connector shown in Fig. As the channel is interrupted in the connector, the second and third enclosed spaces do not communicate with each other. The connector permits fluid flow from the second enclosed space when the piston actuator is in the second longitudinal position. And between the third enclosed space and the piston actuator when the piston assembly is in the first encapsulated position. At this first longitudinal position, due to the low pressure in the channel [825], a small overpressure still present in the actuator piston establishes fluid flow into the third enclosed space. The piston begins to be depressurized and is free from the walls of the chamber or simply coupled with the wall, but does not seal the volume of the upper piston from the lower volume. During the return stroke, the rotation of the crankshaft 852 closes the communication between the second and third enclosed spaces with the piston actuator. When the piston reaches the second enclosed space, the communication with the second enclosed space is opened. The actuator piston will be depressurized and the second enclosed space will be under pressure by the pressure reservoir and the relief valve and consequently the flow of fluid will be in the direction of the actuator piston. The pressurized piston expands in the chamber and is subjected to a reaction force in restoration by force on the wall. This force drives the actuator piston up to the first longitudinal position. The expansion and movement of the piston to the first longitudinal position is a power stroke.

Figure 19b shows two cylinder motors based on Figure 19a with consuming technology wherein two cylinders are placed in a mirror image with respect to the center line of the connection of the sub-crankshafts. The third enclosed spaces (outlets) of the two piston actuators 800L and 800R communicate with each other through the connection of the two lower crankshafts while the second enclosed spaces (inlets) (With two sub-crankshafts) so that the power strokes of the respective actuator pistons move in the same (0 DEG) direction (synchronously), in accordance with the principle of Fig. ) Is designed.

When more than two cylinders are required in the motor in accordance with this synchronous principle, more cylinders can be added and thus, for example, a connection to the second enclosed space of a cylinder to which another second enclosed space is added To an end not yet used, thereby creating a three-cylinder motor. Then, the third enclosed space of the additional free cylinder may still be connected to the third enclosed space of another additional cylinder, so that the motor can function with the four cylinders. The closed ends of the channels of the sub-crankshafts now shown need to be opened in order to establish communication between the enclosed spaces having identical pressure systems.

19B shows an enlarged view of the left part of FIG. 19B.

Fig. 19Bb shows an enlarged view of the right part of Fig. 19B.

Figure 19c shows a two-cylinder motor based on Figure 19a in a pressurizing process comparable to Figure 19b. Figure 19c shows that the configuration of the motor with pistons operated synchronously can be different from the motors in which the pistons are installed in the same direction (0 [deg.]). 19C, the power strokes of the piston actuators are generated at the same instant, but the orientation of the actuator piston 800L is rotated over 180 degrees. The re-orientation takes place in all of the connections to the crankshaft, such as in the direction of the conical chamber, in which the piston actuator moves, and consequently the power stroke is oriented in the opposite direction. Each second enclosed space in the lower-crankshafts is connected to the pressure storage vessel by a channel 829 and the enclosed spaces communicate with each other by an external channel 825. [ The third enclosed spaces communicate with each other through the outer channels to assist flow from the actuator pistons to the piston pump. In the connection of the two lower-crankshafts, the enclosed spaces are shut off and there is no communication between the piston assemblies 800L and 800R.

Figure 19ca shows an enlarged view of the left part of Figure 19c.

Fig. 19cb shows an enlarged view of the right part of Fig. 19c.

Figure 19d shows a two-cylinder motor, based on Figure 19a, in which the piston actuators operate asynchronously. When the piston assembly 800L is started in the return stroke, the piston assembly 800R is started with a power stroke. As a result, when the other piston actuator is in the first longitudinal position, one piston actuator is in the second longitudinal position, and vice versa. The orientation of the actuator pistons is opposite (180 DEG). As there is a power stroke and a return stroke every moment, the power supply by the motor of Figure 19d becomes steady and to a somewhat (rather) constant level. The enclosed spaces of each cylinder assembly are not connected through the sub-crankshafts, and the pressurized channel 829 communicates with the two second enclosed spaces. The channel [825] between the third enclosed spaces also communicates with the piston pump 826. Because the openings in the connector from the second or third enclosed space to the actuator piston are different in half of the cycle between the piston assemblies 800L and 800R, the communication by the pressure channels between the piston assemblies . As there is no communication through the connections between the lower-crankshafts, the channels 825 and 829 are external.

Fig. 19d shows an enlarged view of the left part of Fig. 19d.

Figure 19db shows an enlarged view of the right part of Figure 19d.

Instead of the toothed belts at the power side of the motor, the drive of the pump (s) may be very well exchanged by the gears.

19620 Description of Preferred Embodiments

Figure 21A shows a so-called constant maximum force chamber 1, with a wall section 2 in the longitudinal section, at a first longitudinal position of the piston (not shown), parallel to the central axis 3. A portion (4) of the chamber wall has a convexly formed wall in the longitudinal section of the chamber (1). There is a transition 5 of the longitudinal cross section of the outer wall of the chamber from the convex wall portions 4 to the concave wall portions 7. The wall portion 6 disposed at the second longitudinal position of the piston (not shown) is not parallel to the central axis 3 of the chamber 1. The overpressure of one bar is applied to the common boundary 9 (FIG. 1) of the longitudinal cross-sectional area section 10 of the chamber 1 at a longitudinal position reached by the piston (not shown) when moving from the first longitudinal position to the second longitudinal position ). (11/13/15/17/19) between the longitudinal cross-sectional section sections 12/14/16/18/20/22/24/26/28/30 of the chamber 1 in the longitudinal position / 21/23/25 and 27, respectively, for example, in the advanced bycycle pump, by a piston (not shown) / 7/8/9/10 The overpressure on the bar atmospheric pressure is reached. In the case of a ten bar (overpressure) pump, the inner walls of the longitudinal cross-sectional sections 28, 29, 30, 31, 32, 33, 34, 35 and 6 are convex, while the longitudinal cross- (Overpressure of 6 to 7 bars). When following the mathematical formula slavishly - this is done for design purposes - the outer shape of the chamber (36-37-38) is shown in dashed lines, thereby avoiding the chamber being heavily visible at the top. Such adaptation does not affect the maximum working force, which is a function of the hyperbolic function (measured from the first longitudinal position to the second longitudinal position, as a result of the shape of the chamber along the length, The force is acting at the beginning of the. Due to the small and constant size of the wall thickness over the entire length of the chamber, this is also the case for the outer walls of longitudinal cross sections (not numbered): see WO / 2008/025391.

The longitudinal orientation of the common boundaries may be determined mathematically as a result of the maximum value of the pressure of 10 bars in this figure and the remaining volume of the administrative volume of the conical chamber below the piston. The distances between the common boundaries, which are counted from the first longitudinal position of the piston to the second piston positions, are reduced as the overpressure rate increases. This is also the case for the respective walls of the longitudinal cross-sectional sections 28, 29, 30, 31, 32, 33, 34, 35, 6 and 7. The positions of the walls at the common boundaries are based on the selected value of the maximum working force - in this case 25 kgf (250 N). The characteristic shape (1) of the chamber is the result (WO / 2008/025391).

Figure 21b shows the shape of the 10 bar (overpressure) chamber of Figure 21 (continuous line) and the shape of the 16 bar (overpressure) chamber (dashed line) for the same length of chamber. If the transitional size of the inner diameter of the part 30 can cause problems for the size of the piston, by recompressing the chamber sizes by increasing the maximum value of the work force by the unchanged maximum value of the overpressure Can be achieved. This will, for example, cause the diameter of reference numeral 30 to be larger. Although the thickness in the concave portion 7 may be slightly larger than the wall thickness of the rest of the wall, the wall thickness is substantially uniform over the length of the chamber. If the maximum overpressure has to be greater than 10 bar, for example 16 bar, then another recalculation can be made. This may be achieved by selecting a larger maximum working force such that the circumference of the cross section can be larger. This means that the conical outer wall of the chamber may be closer to the second longitudinal positions before the outer periphery reaches its minimum value, to ensure that the piston is not jammed, as defined by the piston type do. The calculations can be followed exactly in the vicinity of the first longitudinal positions and the size of the chamber can be too large and this is why it is possible to define the shape so that the perimeter begins to become smaller - The same may be true for common boundaries.

Challenges for optimizing the chamber for demands towards handpumps may be made in a manner similar to that described above. The problem to be solved here is that the minimum size of the outer circumference of the inner chamber wall (depending on what the piston performs) at the first longitudinal positions, which is the maximum working force the user holds the handle and which is the designated work force, It is a good trade-off between the outer maximum circumference.

Figure 22a shows the lower end portion of the chamber of the advanced bicycle floor pump and here also the lower end portion of the chamber 1 of Figure 21 can be seen. The chamber 1 is mounted on a foot 41. A flexible manchet 42 assembles the chamber onto the foot 41. The hose 43 is connected to the outlet 44 of the pressure expansion vessel 49 - such an outlet does not have a check valve. A piston 45 (shown schematically) includes a piston rod 46. A check valve 47 is disposed at the lower end of the piston rod and such a check valve communicates with the outside atmosphere 48 and opens toward the chamber 1 so that the piston 45 is moved from the second longitudinal position The chamber 1 is filled when moving to the first longitudinal position. An expansion pressure vessel 49 is shown with the chamber, which includes an inlet check valve 50, and when the inlet check valve is opened, the chamber 1 is connected to the hose 43 via the outlet 44 Communicate. A cross-section of the outer wall 51 of the inflation pressure vessel 49 is shown, together with the inner wall 52. An expansion pressure vessel 49 is assembled between the upper end 53 and the lower end 54 of the vessel 49. The upper end 53 of the expansion pressure vessel 49 is sealed to the wall of the chamber 1 by the O-ring 55 while the upper end 53 and the lower end 54 are sealed to the gas sealing threads 58 and & 59 to the wall 52 of the inflation pressure vessel 49. As shown in Fig.

This is the preferred embodiment for very high pressures (e.g., 16 bar), and where the piston has difficulties sealing against the inner chamber wall. This configuration avoids sealing on the transition from a longitudinal cross-sectional section with a convex wall to a longitudinal cross-sectional section with a concave wall - see FIG.

Figure 23 shows another constant force chamber 80 for a maximum pressure of 10 bars with the same source as the chamber of Figure 1, ensuring that the pressurized container type piston does not move at the second longitudinal piston position And the inner wall 81 of the chamber at the second longitudinal piston positions should be chosen to be parallel to the central axis of the chamber.

From the convex walls 82 of the longitudinal cross-sectional sections between the boundaries 83 and 84 to the side wall 81 parallel to the central axis 85 of the chamber 80, corresponding to 0 bar and 7 bar overpressure, 86.2 and 86.3, respectively, between the common boundary 84 corresponding to the 7 bar overpressure up to the cavity boundary 88 for the 10 bar overpressure, And has a concave shape (86). The shape of the inner wall of the chamber and its outer wall may no longer correspond to each other: 7 between the common boundary 84 for bar overpressure and the common boundary 88 for 10 bar overpressure, the outer wall is still convex On the other hand, the inner wall is recessed. The difference in this shape is that the chamber has its weakest spot: at the transition from the concave inner wall sections to the inner wall parallel to the central axis of the chamber, the remaining wall thickness of the chamber wall thickness Thereby making it possible to increase the wall thickness. The outer wall 89 of the chamber, in which the inner wall of the chamber is located parallel to the central axis of the chamber, may be selected as a straight line, but is not necessarily parallel to the central axis. This may be done for the purpose of looking good, as the curved shapes provide some visible tension.

The transition from the concave inner walls to the inner wall of the chamber parallel to the central axis of the chamber may be made smooth so that the piston can pass through the transition without jamming.

Figure 24 shows a foot 70 of an advanced floor pump for tire inflation, for example. The flexible monantheette 71 holds the conical chamber 80 of Fig. 3 in place. The inner wall 81 of the chamber 80 is parallel to the central axis 85 of the chamber 80. An inflatable piston (73). Enclosed space (66). The tube (65). Inlet check valve (75). Outlet check valve (76). Hose (77). Measurement space 78, 79 (inside the hose). Valve connector 67 (not shown). The space 68 inside the valve connector 67 is also part of the measurement space (not shown).

25 shows chamber 100, which is a 10 bar overpressure chamber of chamber 1 of Fig. The second longitudinal positions are terminated with a cavity boundary 27. This lower end of this chamber is screwed onto a lower end portion 101 corresponding to the longitudinal cross-sectional section of Fig. The thread connecting the two parts of the chamber is the gas thread 102, which creates a hermetic connection. An outlet 104 is present at the lower end 103 of the chamber part 100 and the hose nipple 105 is screwed into such an outlet. The chamber portion 100 includes a piston 106 shown schematically. The piston 106 includes a hollow piston rod 107 that includes a check valve 108 that opens a space 109 between the piston and the lower end 103, So that it can be introduced into the space 109 from the atmosphere 48. The hose nipple 105 is a hose 110 assembled with a hose clamp 111. The hose is connected at its other end to valve connector 67, for example. Hose 112 in hose 110.

19630 Circular chamber design

DESCRIPTION OF THE PREFERRED EMBODIMENTS

Figure 30A shows the circular chamber of Figure 12B, wherein the piston moves within the non-moving chamber. The circular lower chamber 961 has a circular round section line 961 that is closest to the center point 967 of the circular chamber 960 in the straight body 982 that is faster than the postal matter 983 in which the line 981 is located. 0.0 &gt; 980 &lt; / RTI &gt; A radius line 987 between the circular center 980 and the circular section line 981. The circular round section line 984 of the circular lower-chamber 961 furthest to the center point 967 of the circular chamber 960 has a center point 985 in the postal matter 986 that follows the line 984, ). A radial line 988 between the circular center 985 and the circular section line 984. This may be valid for both of the other lower-chambers 962, 963, and 964. These circular round section lines may be circular section lines in other preferred embodiments.

Figure 30B shows the circular chamber of Figures 13C and 14D, wherein the piston does not move and the chamber moves. Here, the design of the circular chamber and the sub-chambers is identical to that of FIG.

FIG. 31A shows FIG. 14D, wherein a section X-X of the chamber 1749 and through the central axis 1750 is shown.

Figure 31B shows an enlarged view of the detail of section X-X of chamber 1749 of Figure 31A. A chamber wall 1785 is shown in section X-X. Wall 1785 includes each of ducts 1786, 1787, 1788, 1789, 1790, 1791, 1792, 1793, 1794, 1795, 1796, and 1797 having openings towards chamber 1749. Preferably, no duct is present near where X-X meets the farthest end face from the center 1750 of the circular chamber 1749. Thereupon, around the periphery of the chamber 1749, the widths of the ducts from both sides 1786/7/8/9/90/91, and 1796/5/4/3/2/1 of the line of section XX And the duct 1791 has the largest width. The ducts are substantially identical to the circumference of the contact area of the piston and the wall 1785 within the chamber 1749, so that they can be piston-steered through the circular chamber in the direction of the circular chamber, The size of the contact area of the wall 1785 of the chamber 1749 with the piston is reduced so that adequate repulsive force can be obtained.

Figure 32A shows a plane orthogonal to the base circle intersections in the circle where the walls and center of the chamber are located within the base circle.

32B shows a section of the boundary of the piston.

Figure 32c shows the values of a and h only - see the formulas (2.1) and (2.2) - the radius of the imaginary sphere is given in (2.3) Lt; / RTI &gt;

Figure 32d shows the piston with end caps.

Figure 32E shows the piston with end caps inside a transparent Fermi-tube hammer.

Figure 32f shows the pure contact area between the chamber and the piston, which can be seen inside the transparent chamber wall.

Figure 32g shows the contact area between the piston and the chamber.

Figure 32h shows a section of the chamber wall. The chamber reaction force is marked gray (1800). The total force on the section is orthogonal to the chamber wall. In such a section, the value of the force is proportional to the (variable) longitudinal length of the section shown and to the internal pressure of the piston.

The lcoal reaction force from the chamber wall is proportional to the longitudinal width of the section, which again is linear in the distance to the center of origin, the center of origin. The length up to the first order is changed around the section as in a tube with a certain radius. The length depends linearly on the distance to the origin. The local force is changed accordingly and therefore the force is adjusted to drive the entire wall and hence the piston as a pure rotation around the origin. Fermi composition. The generator sources have an orthogonal plane at each point as shown. The chamber walls intersect all such orthogonal planes in a circle centered at the generator source. The chamber walls are 'conical' when selecting the radius of the circle in the orthogonal plane to have a linear (or simple increase) value as a function of the arc length along the generator circle.

Figure 32i shows the cross section of Figure 32h, with an additional cross-section for providing an open view.

Figure 32j shows Figure 32h, and the red 1801 vector is a component of the gray force 1800 along the length direction.

Figure 32k shows a cross section of Figure 32j with an additional cross-section for providing an open view.

Figure 32l shows Figure 32j, where the actual sliding force along the wall is shown in blue 1802 - which is obtained by projecting a red 1810 vector orthogonal to the chamber wall.

Figure 32m shows the cross section of Figure 32l, with an additional cross-section for providing an open view.

19640 Description of Preferred Embodiments

40A shows a longitudinal section of a pump 1500 having a piston 1501 including a U-shaped support means 1502, an O-ring 1503 and a flexible impermeable layer 1504, The flexible impermeable layer 1504 is supported by the foam 1505 in a first longitudinal position of the chamber 1506. [ The support means 1502 is rotatably coupled to the piston rod 1507 using a suspension 1508, including an axle 1510. A pulling spring 1509 is fastened to the piston rod 1507 on the axle 1510 and to the other end on the support means 1502 closer to the O-ring 1503. The horizontally disposed spring 1511 supports the O-ring 1503. Impermeable flexible sheet 1504 includes a layer having reinforcement portions 1514 (only one shown in Figures 40b, 41d, and 41e) vulcanized on the layer without reinforcement portions 1513. [ Central axis 1518 of chamber 1506. An angle (?) Between the center axis 1518 and the line connecting the center of the O-ring 1503 to the center of the axle 1510. An impermeable flexible sheet that is not stressed by loading from the fluid in the chamber 1506 is perpendicular to the central axis 1518 of the chamber 1506.

Fig. 40B shows the impermeable flexible sheet 1504 vulcanized in the O-ring 1503. Fig. A layer 1513 having no reinforcing portions and a layer 1512 having reinforcing portions 1515 are vulcanized at the top of each other. The support means 1502 and the horizontal spring 1511 are vulcanized on the O-ring 1503 and the layer 1513 of the impermeable sheet 1504. The end of the support means 1502 has a small bended flat surface 1516, to which the shape of the O-ring 1503 is fitted when produced. O-ring 1503 is squeezed on wall 1517 of chamber 1506.

Figure 40c shows the longitudinal section of Figure 40a in a second longitudinal position. A piston rod 1507, a wall 1517, and a central axis 1518 of the chamber 1506. The support means 1502 was rotated around the axis 1510. [ The foam 1505 'was squeezed. The spring 1509 'is pulled longer. The size of the O-ring 1503 was increased and still pressed against the wall 1517 of the chamber 1506. The thickness of the impermeable sheet 1504 'is increased while the horizontal spring 1511' is pressed together. Angle (beta) between the center axis 1518 and the line connecting the center of the O-ring 1503 to the center of the axle 1510.

41A is a top view of the piston 1501 of FIG. 40A and a cross-section of the chamber 1506 from a first longitudinal position. Wall 1517 of chamber 1506. Piston rod 1507. Suspension 1508 of the support means 1502. Axle 1510. Pull springs (1509) of the support means (1502).

중심 축에 평행

Parallel to the central axis

The foam may include stiffeners that can be rotationally fastened to the piston rod.

Figure 41B shows the details of the suspension of the support means 1502 on the O-ring 1503 and the lying spring 1511 of the piston 1501 of Figure 40A. A small bended flat surface 1516 at the end of the support means 1502 that is vulcanized on the O-ring 1503. The end 1519 of the support means 1502 has a notch 1521 which is fitted with the size and shape of the horizontal positioning spring 1511. At the end of the boundary 1520-support means 1502 of the deployment spring 1511, the spring is shown only partially.

Figure 41c shows a cross-section of chamber 1506 with piston 1501 of Figure 40a in a second longitudinal position. The support means 1502 is a suspension 1508.

Figure 41d shows the spiral reinforcement 1522, 1523, 1524 of the flexible impervious sheet 1504 - the material is flexible. These spirals are shown generally concentrically relative to each other, at a certain distance, about the central axis 1518 of the chamber 1506. [ Two layers may be possible with different configurations, for example, reinforcements that can intersect each other at a small angle, but this is not shown.

41E shows another reinforcement configuration, i.e., more or less elastic reinforcement members 1525, concentrically disposed about the central axis 1518 of the chamber 1506. [

42A shows a longitudinal section of a piston 1530 including a support means 1502, an O-ring 1503 and a flexible impermeable sheet 1531, the flexible impermeable sheet 1531 having a cross- At a first longitudinal position, with a central axis 1518 of the chamber 1506 at a certain angle [lambda]. The sheet 1531 is vulcanized on the piston rod 1507 (1532). An angle (?) Between the center axis 1518 and the line connecting the center of the O-ring 1503 to the center of the axle 1510. The flexible impermeable sheet 1531 has an angle y with respect to the central axis 1518 of the chamber 1506.

Figure 42b shows the detail of the suspension, O-ring 1503 and flexible impermeable layer 1531 of the support means 1507 which have been vulcanized together. While the top layer 1533 includes reinforcements (the same as reinforcements in Figures 41d-e), the bottom layer 1534 does not have reinforcements. Angle (beta) between the center axis 1518 and the line connecting the center of the O-ring 1503 to the center of the axle 1510.

Figure 42c shows a longitudinal section of the piston 1530 of Figure 42a in a second longitudinal position. The angle? Between the flexible impervious sheet 1531 and the center axis 1518 of the chamber 1506 is as follows.

19650 Description of the Preferred Embodiment

50 shows a suspension within each of three rows of holes 1240, 1241 and 1242 of a holder 1224 and stiffeners 1208, 1209 and 1210 in the holder 1224, respectively. Note that the longer each stiffener 1208, 1209, 1210, the longer each of the smaller bent ends 1220, 1221, 1222 and the stiffener is longer. Hole in piston rod (not shown). Center axis 1244. A foam 1245 of the piston 1200.

Figure 51 shows the piston 1200 of Figure 50 shown in a first longitudinal position 1204 of the chamber 1202 and configured in a pump 1201 having a chamber 1202 and an upper portion 1203. The upper portion 1205 has a bearing 1206 through which the piston rod 1207 moves. The bearing 1206 is assembled in the upper portion 1203. The chamber 1202 is of a type in which the force is pressure independent (see 19620). A wall 1207 of the chamber 1202. Each of the stiffeners 1208 (1209 dashed line), 1210 each has a free end of each of the increased diameter 1211, (1212), 1213, respectively. The impermeable layer 1214 is closed by the clamp 1215 to the piston rod 1207 while in the top 1216 of the piston 1200 and the foam is sealed by the fluid in the chamber 1202 from the uncompressed side 1202 ' . The stiffeners 1208, 1209, 1210 each have bent portions 1217, 1218, 1219 and miniature bent ends 1220, 1221, 1222, respectively. Each of the miniature curved ends 1220,1221,1222 is connected to an adjustable member 1223 rotatable within a holder 1224 which is sealed to the piston rod 1207 by an O- . &Lt; / RTI &gt; The adjustment member 1223 is rotatable within the holder 1224 and is sealingly connected to the impermeable layer 1214. The piston 1200 is assembled on the piston rod 1207 by a holder 1224 mounted within the spring ring 1225 while the clamp 1215 is mounted on the spring ring 1226. [ The central axis 1243 of the chamber 1202.

Fig. 52 shows the bent portion 1218 of the stiffener 1209. Fig. Increased diameter 1212 of stiffener 1209. Chamber 1202. End 1221.

19650-1 Description of the Preferred Embodiment

Figure 55a shows a piston 1300 in a first longitudinal position of the progressive pump and the piston 1300 is in the vicinity of the piston rod 1306 in the direction toward the compression side of the piston 1300, A foam 1301 having metal reinforcing fins 1302, 1303 and 1304 positioned in a circular column and an impermeable layer 1305 around the foam 1301, And is magnetically coupled to the magnetic holder plate 1307 of the holder 1308 mounted on the holder 1308. The holder plate 1307 is mounted on the holder 1308, adhered or otherwise mounted. The holder 1308 may be rotatable about a piston rod 1306 and may be supported by two spring plates 1310 and 1311 that fit within respective notches 1312 and 1313 of the scraper piston rod 1306 And is fastened longitudinally to the piston rod 1306. The metal of the pin can be magnetized. The foam 1301 can be manufactured as an open cell, preferably a PU foam (as described in Section 19650 of this patent application) - the venting of the open cell is described in Figure 55b. The holder 1308 has a gland 1317 for the O-ring 1318 that seals the holder 1308 against the piston rod 1306. The central axis 1319 of the piston 1300. The impermeable layer 1305 can be made of natural rubber (NR), and when the size and shape of the manufacture are located in a second longitudinal position of the chamber (not shown), the size of the exterior of the piston 1300 ' Shape. That is, the impermeable layer 1305 expands as the piston 1300 'advances toward the first longitudinal position by the force of the inflating foam 1301. The reinforcing pins 1302,1303 and 1304 may have a thin layer of PU (not shown) which allows the PU foam to be better retained on the pins 1302,1303 and 1304. This surface treatment can be done, for example, by immersing the pins 1302, 1303, 1304 in a PU foam fluid. Arrow 1335 shows how the foam is squeezed toward the piston rod 1306 as the piston 1300 advances toward the second longitudinal position, where the piston has the reference numeral 1300 '. Low pressure side 1315 of piston 1300 and atmosphere 1316.

55B shows an extended longitudinal section PP of the hold plate 1307 mounted on the holder 1308. Fig. A central axis 1325 of the holder 1308. The holder plate 1307 is made of a magnetic material, for example, by compressing a metal powder and then backing it. Above the holder 1308 is a vent channel 1314 having a central axis 1321 (see also Fig. 55C) through a channel 1320 of the holder plate 1307 (see Fig. 55C) 1315 to the atmosphere 1316 to allow communication of the fluid in the open cells to and from the uncompressed side 1315 of the piston 1300. [ This configuration is also used in Figures 55E to 55H.

55C shows an enlarged view of the holder plate 1307 on the holder 1308. Fig. The underside of the holder plate has three rows 1326, 1327 and 1328 of small closed rounded end holes 1329, 1330 and 1331, respectively, in which the metal pins 1302 , 1303, and 1304 are held. The ends can be rounded so that they are better fit within each of the end holes 1329, 1330, and 1331. [ The rounding of the end holes and the side-radius of the &quot; log &quot; hole are slightly greater than the diameter (not shown in this figure) of each of the pins 1302,1303 and 1304, To rotate within a plane including the center axis of the holder 1308. [ The center of the rounded end hole lies in all pivots perpendicular to the central axis of the holder 1308. [ The left sides of the end holes 1328, 1330 and 1331 are connected to the respective rounded sides of the end holes 1329, 1330 and 1331 so as to guide the upper portions of the respective pins 1302, 1303 and 1304, Not as deep as the right side of. Between the holder 1308 and the holder plate 1307 there is a small circular recess 1332 of the holder 1308 which is held by the holder 1308 by a screw Impermeable layer 1305 to be pressed between holder 1308 and holder plate 1307 when fastened to holder 1308. As shown in FIG.

Figure 55d shows an enlargement of the projection 1333 in the recess 1332 for improved squeezing of the impermeable layer 1305 (not shown). This configuration is also used in the embodiments of Figs. 55E and 55G, which are enlarged in Figs. 55F and 55H, respectively.

Figure 55E shows an alternative solution to that shown in Figures 55A-55D. New reinforcement and fastening of the foam 1351 (not shown) of the piston 1350 (not shown) to the holder 1359 is shown in detail in Figure 55f. The piston 1350 is located in a first longitudinal position of the progressive pump. The ventilation channel 1314 is identical to that described in Figures 55b and 55c.

Fig. 55F shows an enlarged view of the holder plate 1358 and the holder 1359. Fig. The piston 1350 is rotatably fastened to the spherical ends 1355, 1356 and 1357 of the holder plate 1358 in the respective spherical cavities 1360, 1361 and 1362 of the holder 1359 (1352, 1353, 1354) as reinforcement of the foam, preferably made of the same material as PU-, as described in Figure 55A, And is mounted on the piston rod 1306 as described in the description of 55a. The holder plate 1358 further includes each of the other openings 1363, 1364, 1365 for guiding each of the pins 1352,1353, 1354, respectively. The pins 1352, 1353, and 1354 may have a non-uniform thickness to maintain the foam better. The optimized configuration is such that the piston 1300 does not squeeze the foam between the pins 1352, 1353, 1354 near the roughened spherical ends as the pins 1352, 1353, 1354 rotate counterclockwise, In order not to get closer to each other when proceeding to the bi-directional position, the thickness non-uniformity may begin slightly earlier than the spherical ends 1355, 1356, 1357 as shown earlier in the drawing. See FIGS. 55C and 55D for the description of fastening of the impermeable layer 1305 between the holder 1359 and the holder plate 1358. FIG.

Figure 55g shows an alternative solution to that shown in Figures 55e and 55f with a holder 1365 and reinforcing pins 1366,1367 and 1368. [

Figure 56h shows an enlarged view of the holder 1365 including a holder plate 1369 and a circular disc 1370 made of a flexible material. The reinforcing pins 1366,1367 and 1368 are arranged such that the pins 1366,1367 (and possibly also 1368-not shown here) are connected to the pins 1371,1367 , 1372 (and 1373 - not shown), respectively, as shown in Figures 56 (a) and 56 (f). The pins 1372 and 1372 are secured into the elastic disc 1370 and cause the pins 1352,1353 and 1354 to automatically rotate clockwise as the piston advances to the first longitudinal position.

19660 Description of the Preferred Embodiment

60 shows an enlarged container-type piston 1400 in a chamber 1401 having a central axis 1402 at the start and end of a stroke. The chamber is of a type in which the force on the piston rod is approximately uniform during stroke. The shape of the piston in the second longitudinal piston is the shape of the &quot; starting &quot; ellipsoid 1403 after being compressed from the stress-unfavorable manufacturing model, where the shape is substantially cylindrical (see FIGS. 61 and 62). The shape of the piston in the vicinity of the first longitudinal position is the final ellipsoid 1404 which is substantially a sphere 1405 (dotted line). Between them there is a piston 1400 in the shape of an ellipsoid. The details of the ellipsoid in place of the sphere at the first longitudinal position are the same as those of the sphere.

61 shows a manufactured container-type piston 1400 in which the stress applied is a stress ratio that can have the shape of an ellipsoid or a sphere. At the bottom of the drawing is an unremovable cap 1420 having a gland 1421 for an O-ring (not shown) tightened on a piston rod (not shown). The recess 1422 is a few glands for an O-ring (not shown) which is threaded through a hole 1432 onto a bolt (not shown) that locks the bottom of the piston rod (not shown) Tighten the bottom of piston 1400. A gland 1424 for an O-ring (not shown) engages the piston on top of the piston 1400. Both caps 1420 and 1423 have recesses 1425 and 1426 respectively and are used to vulcanize the flexible walls 1427 of the container piston 1400 on each of the caps 1420 and 1426. The wall 1427 is shown in the figure with two layers, a layer that functions as a cover 1429 for the reinforced layer 1428 and the reinforced layer 1428. The dashed line shows the possible third layers 1430 and 1431 on top of each of the other layers 1428 and 1429 that are present only at the positions where the two layers 1428 and 1429 are each vulcanized on the caps 1420 and 1423 Respectively. Center axis 1433. The wall 1427 of the piston 1400 is approximately parallel to the central axis 1433. The reinforcement strands 1440 are placed in a parallel pattern parallel to the central axis 1433. The reinforcement pattern 1441 is when there are two layers.

Fig. 61 shows both caps 1420 and 1423 in Fig. 16, respectively. Outside, each of the rounded transition portions 1434 and 1435 extends from the flexible wall 1427 to portions of the wall 1427 which are vulcanized on portions 1425 and 1426 of the caps 1420 and 1423 . On the inner side of the flexible wall 1427 there are rounded transition portions 1436 and 1437 just before the flexible wall 1427 meets the portions of each of the caps 1420 and 1423 respectively. These transition portions 1436 and 1437 provide a stable transition of the wall when the piston is stressed by expansion.

19660-2 Description of the Preferred Embodiment

63 shows the force to the wall 2275 of the chamber 2276 having a different cross-sectional area and a different or the same circumference from the wall of the actuator piston (not shown) and having a central axis 2277. Fig. There is a reaction force 2278 perpendicular to the wall 2275 against the expansion force of the wall of the actuator piston (not shown - see Fig. 64a). During rolling, particularly when sliding the wall of the actuator piston (not shown - see Figure 64a) on the wall 2275 of the chamber, there is a friction force 2281 from the actuator piston. There is a reaction force 2279 of the wall 2275 of the chamber 2276 of the wall of the actuator piston (not shown - see Figure 64a). There is a component 2280 along the wall 2275 of the chamber 2276. The component 2280 is shown as being larger than the frictional force 2281. There is an angle [alpha] between the wall 2275 of the chamber 2276 and the central axis 2277 of the chamber 2276. [

Figure 64a shows an elliptical actuator piston 2285 in a chamber 2286 having a longitudinal central axis 2287 and a wall 2287 of the chamber 2286 is angled with respect to the central axis 2288, Lt; RTI ID = 0.0 &gt; 20 &lt; / RTI &gt; A wall 2289 of the actuator piston 2285 is connectably coupled to a wall 2287 of the chamber 2287.

Figure 64B shows an elliptical actuator piston 2290 in a chamber 2291 having a longitudinal central axis 2292 and a wall 2293 of the chamber 2291 is angled with respect to a central axis 2292, And is shown at an angle of 10 degrees. The wall 2295 of the actuator piston 2290 is connectably connected to the wall 2293 of the chamber 2291. The actuator piston 2290 is shown on three locations 2296, 2297, and 2298 in the channel 2291 and may be configured to be of a size corresponding to, for example, 86.4 mm of the current petrol vehicle cc gasoline-powered automobile) with stroke lengths of less than 10 mm.

19680-2 desirable Example  Explanation

80A illustrates a chamber 2101 (although any other chamber configuration may be used) of the pump in accordance with section 19620 having a central axis 2102 and a piston 2104 according to, for example, an inflatable section 19660 , The wall 2105 of the piston 2104 includes a discrete portion 2106 and a cross section of the wall 2105 of the chamber 2101 And the center line 2102. The center line 2102 has a circular arc shape.

Figure 80b shows an enlarged view of the contact surface 2107 of the walls 2103 of the chambers 2101 and 2108 of the wall 2105 of the piston 2104 when the piston 2104 is in the first longitudinal position, 1) detail and the surface 2108 of the individual wall portion 2106 on the last mentioned surface 2109 can roll and slide. Each of the contact surfaces 2107 and 2108 is sealably connected to a wall 2103 of the chamber 2101 and an inclined wall portion 2109 of the piston wall 2105. The inclined wall portion 2109 is connected to the chamber 2101, And has a minimum circumference smaller than that of the adjacent piston wall 2105 closest to the wall 2103 It is clearly shown that the surface 2105 of the piston 2104 is clear from the wall 2103 of the chamber 2101. The contact surface 2107 of the wall 2103 of the chamber 2102 and the individual wall portion 2106 has an angle f between the central axis 2102 and the chamber wall 2103 and is set to be the same as the contact surface 2108 (2110, 2111) having an angle (b) and an angle (c) with the wall of the chamber that is hermetically pressed against the wall (2103) of the chamber (2101). The individual wall portion 2106 may be pressed against the wall 2103 of the chamber 2101 while the peripheral portion of the wall 2105 of the piston 2104 may be compressed Is retracted from its original position (Fig. 80 (f)). There is a transverse center line 2115 of the piston 2104. There is a center line 2114 of the individual wall portion 2106 through the intermediate portion 2116 of the contact point between the individual wall portion 2106 and the wall 2105 of the piston 2104. There is an angle d between the transverse center line 2114 and the line perpendicular to the central axis 2102 of the chamber 2101. [

For example, the vulcanized contact surface 2127 of the wall of the piston 2104 and the circular portion of the longitudinal cross-section of the individual wall portion 2106 is positioned in the vicinity of the transverse center line 2114 of the individual wall portion 2106 And may be only a portion of the original segment. The adjacent wall 2105 will then be further curved which allows the individual wall portion to remain secured from the wall 2105 thereby causing the adjacent wall 2105 of the piston 2104, 2104 ', 2104 " And the wall 2103 of the individual wall portion 2101. This can also be applied to the individual wall portion shown in Figure 80H and to each of the toroid members 2207 and 2244 in Figures 84B and 84F. 2106 will also be much larger when the piston 2104 is in the first longitudinal position than when the piston is in the second longitudinal position.

80C shows the individual wall portion 2106 when the piston is in the second longitudinal position. Where the wall 2105 of the piston 2104 'is still clear from the wall 2103 of the chamber 2101 but less than when the piston 2104' is in the first longitudinal position (Figure 80b). There is an angle e between the transverse center line 2114 and a line perpendicular to the center axis 2102 of the chamber 2101. [ There is a transverse center line 2115 of the piston 2104 '.

Figure 80d shows that when the piston 2104 is in its second longitudinal position-its position within the circumference of the wall 2105 can be such that the piston 2104 is in the second longitudinal position of the chamber 2101- 2102 is a circular segment of the wall 2105 of the piston 2104 &quot;, wherein the wall (not shown) .

Fig. 80E shows an alternative spherical individual wall portion 2112 of what is shown in Figs. 80A-80C. The advantage is that the wall (not shown) 2103 of the chamber 2101 and the individual wall portions (not shown) of the piston 2104 "are relatively more than in the case of the circular segment shape of the individual wall portion 2106 of Figures 80A- 2112. There may be a lateral center line 2117 of the individual wall portion 2112. In this case,

Figure 80f shows an alternative semicircular shape of the individual wall portion 2113 having the same center line 2114 as the transverse center line 2115 of the piston shown in Figures 80a-80c. The individual wall portions are vulcanized on the piston (enlarged) according to section 19660 when the piston 2104 "is in the second longitudinal position as manufactured.

Figure 80g shows a cross-sectional view of the line 2121 through the longitudinal midpoint of the flexible wall of the piston 2104 &quot;, in order to ensure that the transverse center line 2120 of the individual wall portion 2113 is in contact with the conical chamber. 80f, in which the smallest cross-sectional area is the closest to the portion of the piston 2104 "closest to the second longitudinal position, i. E., To the second longitudinal position, have. Other chamber configurations may provide different positioning of the discrete wall portion 2113 and its transverse center line 2120.

80H illustrates a longer piston 2126 (as shown in FIG. 80G) at a first longitudinal position in which the piston 2126 is inflated. The center line 2122 of the individual wall portion 2123 is connected to a transverse center line (not shown) through the longitudinal midpoint of the flexible wall 2125 of the piston 2126 to ensure adequate contact area with the chamber 2124). Other chamber configurations may provide different positioning of the individual wall portion 2106 on the wall 2125 of the piston 2126. [

80i and 80j illustrate a piston 2130 with a reduced circumference at its transverse center line 2131 as manufactured (and therefore at a second longitudinal position). The center line 2132 of the individual wall portion 2133 is as manufactured. This is especially true in the direction of the first longitudinal position 2139 when the wall 2134 of the chamber 2136 changes from being parallel to the central axis 2138 of the chamber 2136 to be non- As the piston moves from the distal second longitudinal position 2137 of the chamber as shown (according to section 19620 of the present patent application - but any other chamber configuration may be used), the wall 2136 of the chamber 2136 2134 to avoid contact of other portions of the wall 2134 of the piston 2130, which is better than that of the individual wall portion 2133. [ A longitudinal centerline 2135 of the piston 2130.

Figure 81a illustrates a chamber 2101 (although any other chamber configuration may be used) of the pump according to section 19620 having a central axis 2102 and three different longitudinal positions 2140, 2140 ' 2140 &quot;, 2140 &quot;, which are enlarged in accordance with section 19660 , according to FIG. 61, which may be inflatable in the piston 2140, 2140 ' The wall 2141 of the chamber 2101 includes more than one, for example two, separate wall portions 2142 and 2143 each of which has a parallel wall of the wall 2103 of the chamber 2101 (The transition from the distal second longitudinal position to a position closer to the first longitudinal position) and the convex wall (from the transition to the first longitudinal position) It is an adaptable circle segment shape.

Figure 81b shows the individual wall portions 2142 and 2143 which are sealingly connected to the walls 2103 of the chamber 2101 and to the respective slopes 2148 and 2149 of the piston wall 2141 in the first longitudinal position 2145 and 2146/2147 for inclined portions 2148 and 2149 which are smaller than those of adjacent piston walls located closest to wall 2103 of chamber 2101 And has a minimum circumference. The individual wall portions 2142 and 2143 are spaced apart from each other by a certain distance from each other to prevent the wall 2141 of the piston 2140 from engaging and / or sealingly engaging the wall 2103 of the chamber 2101 g. It is preferred that the angle of inclination e of the wall 2103 of the chamber 2101 is closer to the transverse center line 2130 of the piston 2141 than to the individual wall portion 2142 located closest to the second longitudinal position There is an individual wall portion 2143 positioned closer to the first longitudinal position. The position of the individual wall portion may be different from that described above and may be varied to avoid the possibility of rolling the piston 2140, 2140 'on the surface 2103 of the chamber 2101, And depends on the shape of the piston 2140, 2140 'and the inclination (s) of the wall 2103 of the chamber 2101.

81C shows an enlarged detail view of the contact surfaces when the piston 2121 is positioned between the first and second longitudinal positions. There is also no contact between the wall 2136 of the piston 2140 'and the wall 2103 of the chamber 2101.

The angle between the line perpendicular to the wall 2103 of the chamber and the center axis 2137,2138 of the discrete portion -with the inclined wall 2103 of the chamber 2101-is not the same, Notice that it is big.

Figure 81d shows the (enlarged 12.5: 1) piston located at the distal second longitudinal position as manufactured. 80d, it may be a piston 2140 "including individual wall portions 2142 and 2143 in the chamber 2101 (not shown), wherein the wall 2103 (not shown) 2101 (not shown) of the piston 2140 &quot;. The arrows show the transverse center line 2130 of the piston 2140 &quot;.

Figure 82a shows a chamber 2101 (although any other chamber configuration may be used) and a piston 2145 that may be inflatable according to section 19620 with a longitudinal center line 2102, Pistons 2145, 2145 ', 2145 "are shown on three different longitudinal positions, respectively, and piston wall 2146 includes two portions 2147, 2148 each having a different circumference in the transverse plane Where the portion 2147 closest to the first longitudinal position has the largest circumference and the contact regions 2149, 2149 ', 2149 " between the wall 2103 of the chamber 2101 and the piston wall 2146 . The size of the contact area may be different on each of the three longitudinal positions.

82B shows an enlarged (5: 1) detail of the contact area 2149 when the piston 2145 is in the first longitudinal position. There are two piston wall portions 2147 and 2148. The piston wall portion 2147 includes an outer skin portion 2150 having a stepped transition portion 2199 of the wall 2146 from the wall portion 2147 to the wall portion 2148 and terminating immediately below the contact region 2149, Wherein the piston wall portion 2147 closest to the first longitudinal position is closest to the wall 2103 of the chamber 2101 and the wall portion 2148 is closest to the second longitudinal position. Below the skin portion 2150, there may be a layer, preferably another skin portion 2151 which is a reinforcing layer. The skin portion 2151 is preferably present in the entire piston wall 2146. The outer skin portion 2150 of the piston wall portion 2148 and the outer skin portion 2151 located behind the outer skin portion 2151 2152) starts. The contents of the piston may be a fluid, a mixture of fluids or a foam (not shown). There is no contact between the skin portion 2148 of the wall 2146 of the piston 2145 and the wall 2103 of the chamber 2101. The transverse center line 2153 of the piston 2145 is closer to the first longitudinal position than the stepped transition 2199 of the wall 2146 from the wall portion 2147 to the wall portion 2148.

82C shows an enlarged detail of the contact area 2149 'when the piston 2145' is positioned between the first and second longitudinal positions. Here, there is no contact between the skin portion 2151 'of the wall portion 2148' of the piston 2145 'and the wall 2103 of the chamber 2101. It is shown that the contact area 2149 'of the wall 2103 of the chamber 2101 and the wall 2147' may be different from the contact area 2149 of FIG. 82B. A transverse center line 2153 'of the piston 2145'. This center line 2153 'may be located closer to the first longitudinal position than the stepped transition portion 2199 of the wall 2146 from the wall portion 2147 to the wall portion 2148.

Figure 82d shows the (enlarged 12.5: 1) piston 2145 " of the wall of the piston 2145 " positioned in the second longitudinal position - the chamber is not shown. The wall portion 2147 has a diameter? Z, while the wall portion 2148 has a wall portion? Z-z ₁ (z ₁ > 0). Lateral center line 2153 "of piston 2145 &quot;.

Figure 83a shows the piston 2121 "of Figures 82a-82d as manufactured in the second longitudinal position.

83B shows the piston 2121 of FIG. 83A in a first longitudinal position, wherein the piston 2121 is inflated through its piston rod 2151 - arrow 2152.

Figure 83c shows the piston 2121 of 83b even in the first longitudinal position where the piston 2121 is positioned such that the position of the movable cap 2154 is fixed on the piston rod 2151 by the clamp 2155 Then retracted through its piston rod 2151 - arrow 2153.

83D illustrates the piston 2121 of FIG. 83C in a first longitudinal position wherein the cavity (not shown) 2156 of the piston 2121 is connected to a piston rod (not shown) (Polyurethane) as a mixture of a memory PU foam type (see section 19640 of the present patent application) and a standard PU foam type, as shown in the arrow 2157. This foam is preferably filled through a sealed space 2159 of the PU foam (polyurethane) - it is a good compressible foam with an open cell structure.

83E shows the piston 2121 of FIG. 83D in a first longitudinal position, wherein a cavity (not shown) 2156 of the piston 2121 is located in the form (Not shown). For example, compressing the wall 2146 of the piston 2121 by moving the piston rod 2151 including the piston 2121 from a first longitudinal position to a second longitudinal position without much force It is now possible.

It may be necessary to add a compressed fluid such as a gaseous medium through the open cell of the foam to achieve a suitable sealing force for the piston and / or an appropriate compressive force.

83F shows the piston 2121 " having its now-compressed foam (not shown) 2158 inserted in Fig. 83D and its piston rod 2151 and the enclosed space 2159 of the piston 2121 " And a combined pressure sensor 2160 and an expansion valve 2161 according to FIG. 3B of WO2109 / 083274 for a cavity 2156 (not shown) and a cavity 2156 (not shown). The piston rod 2151 may preferably be of a type having a constant volume (WO 2110/094317) in which the enclosed space (not shown) 2159 is optionally of a type having a variable volume according to WO 2100/070227 .

83g shows an enlarged view of the combination sensor-expansion valve device of FIG. 83f. The expansion valve 2161 has an inlet 2196 for the sealed space 2159 of the piston rod 2151. The inlet of the pressure sensor 2160 and its outlet 2195 according to WO2111 / 000578.

Figure 83h shows the relationship between the piston 2121 " with the inserted foam (not shown) 2158 of Figure 83d and the cavity 2156 " (not shown) of the piston 2121 &quot; The combined pressure sensor 2162 and the expansion valve 2161 according to FIG. 5 of WO2111 / 000578 for space 2159 (not shown). The piston rod 2151 preferably has a type in which the enclosed space (not shown) 2159 has a constant volume (WO 2110/094317), optionally a variable volume according to WO 2100/070227.

Figure 83i shows an enlarged view of the combination sensor-expansion valve arrangement of Figure 83h. The expansion valve 2161 has an inlet 2196 for the sealed space 2159 of the piston rod 2151. The inlet of the pressure sensor 2162 and its outlet 2197 according to WO2111 / 000578.

83J shows the piston 2121 " having the inserted foam (not shown) 2158 and the piston rod 2151 and the cavity 21516 (not shown) of the piston 2121 " The combined pressure sensor 2164 and expansion valve 2165 according to FIG. 9 of WO2111 / 000578 for space 2163 (not shown). The piston rod 2151 preferably has a type in which the enclosed space (not shown) 2163 has a constant volume (WO 2110/094317), optionally a variable volume according to WO 2100/070227.

83K shows an enlarged view of the combined sensor-expansion valve device of FIG. 83J. The expansion valve 2165 has an inlet 2198 for the sealed space 2163 of the piston rod 2151. The inlet of the pressure sensor 2164 and its outlet 2199 according to WO2111 / 000578.

83D for expanding the wall 2146 of the piston 2121-the spring 2166 that pulls the movable cap 2154 toward the fixed cap 2167- is set to its default size of the PU foam Expansion adds the force for the expansion. The spring 2166 is positioned on the piston rod 2151 and is attached to the movable cap 2154 and the fixed portion 2168 located in the configuration 2168 of the piston rod 2151.

In order to solve the problem that the volume of the expanded ellipsoid is much larger than the volume of the compactly enclosed space, that is to say of the piston rod, the expanded volume can be substantially reduced by the expansion of the wall of the piston, . This means that when the expanded piston is urged from the first longitudinal position to the second longitudinal position, the rise of the internal pressure is small, allowing the piston to be reduced in size (without jamming).

84A shows a state in which the both elastic flexible walls 2175 of the piston 2170 are engaged with the center shaft 2171 and the piston rod 2172, the fixed cap 2173 and the movable cap 2174, And the wall 2175 has a stiffening layer 2176. The stiffening layer 2176 has a stiffening layer 2176. The stiffening layer 2176 has a stiffening layer 2176, The piston 2170 has a wall of the type shown and described in Figures 82a-82d. The wall 2175 has a U-shaped arch vault 2177 in which an expansion torus 2178 having a wall 2179 with a reinforcement 2180 is located, The circumferential size of the sieve 2178 is increased by the higher internal pressure without decreasing the outer cross-sectional diameter d, and is reduced by the lower pressure. This is because the wall 2175 'of the piston 2170 is approximately parallel to the central axis 2171 and the toroid 2178' is substantially parallel to the central axis 2171 when the piston 2170 is in the second longitudinal position of the chamber ) Is located adjacent to the piston rod 2172 and the wall 2175 having a restricting portion 2181 for providing space in the toroid 2178 '. The wall 2179 of the toroid 2178 is much thicker than when the piston 2170 is in the first longitudinal position with the reinforcement 2180 having an angle greater than 54 ° 44 ' The flexible hose 2182 communicates with the enclosed space 2183 of the piston rod 2172 through its channel 2190 and communicates with the channel 2184 in the toroid 2178 at the other end of the channel 2182. [ ). The U-shaped arch ceiling 2177 guides the toroid 2178 when the piston is between the first and second longitudinal positions. When the piston 2170 moves from the second longitudinal position to the first longitudinal position, a traction spring 2185 is positioned between the piston rod 2170 and the piston rod 2170 to reduce the force required for expansion of the wall 2175 of the piston 2170. [ 2172 and is attached to the movable cap 2174 and a hook 2186 is fastened within the restraining portion 2181 of the piston rod 2172. [ When the piston 2170 is in the second longitudinal position of the chamber, a small diameter of the channel 2184 'inside the toroid 2178' is observed. The cross section of the flexible hose 2182 has its channel 2190. The channel 2190 communicates with the space 2183 sealed at one end thereof and communicates with the channels 2184 and 2184 'at the other end thereof. In the high-pressure side (2187) has inner (2192) of the wall (2175 to 2187) of the piston (2170) of the wall (2175) of the piston (2170) a form (2193) (e.g., a section of the present patent application 19 630 And a PU foam of the kind used in the foam piston). Because the foam 2193 has an open cell, it is connected to an enclosed space 2183 (not shown), or preferably to a low pressure side 2188 (not shown - or see FIG. 84b) Pressure side 2191 of the gas-liquid separator. The toroids 2178 and 2178 'are shown with a central axis 2194 converging with the transverse center axis 2195 of the piston 2170 to obtain an optimal ellipsoidal wall 2175. The high pressure end of the piston rod 2172 is shown with a pressure sensor as described in Figure 83h / 83i.

84B shows an elliptical type piston 2200 of an improved and simplified version of the piston 2170 of FIG. 84A wherein the entire interior 2201 in the wall 2202 of the piston 2200 is shown in FIG. 84A And the PU form 2203 described in FIG. Within the wall 2202 of the piston 2200 is a channel 2205 mounted (e.g., by vulcanization) inside the wall 2202. The channel 2205 communicates with the channel 2206 of the toroid 2207 at one end and with the enclosed space 2208 of the piston 2200 in the piston rod 2209 at the other end. The foam 2203 is in communication with the space 2208 enclosed by a channel (not shown) or preferably through a channel 2211 in the movable cap 2212 to the low pressure side 2210 of the piston 2200, And communicates with the high pressure side 2211 of the piston 2200 (not shown). The toric member 2207 is shown with a central axis 2213 converging with the transverse center axis 2214 of the piston 2200 to obtain an optimal ellipsoidal wall 2202. However, the contact surfaces 2107, 2108 of the discrete portion 2106 with the central axis 2114, due to the shape of the chamber 2104, 2104 (as shown in Figures 80A-80C, 80H) 2115 are positioned closer to the second longitudinal position of the chamber than the transverse center axis 2115 of the piston 2200. The center axes 2114, (Not shown) of the cylinder (not shown), it can also be applied to the contact area of the wall of the chamber (not shown) and the toroidal body 2207. The piston The high pressure end of the rod 2209 is shown with the pressure sensor described in Figure 83h / 83i.

84C shows the piston 2220 having the same configuration of the piston 2170 of Fig. 84A, except for the wall 2221 on the low-pressure side of the piston 2220. Fig. The wall portion 2221 is not a portion of the ellipsoid as shown in Fig. 84, but a portion of the cone shown under tension.

84D illustrates a spherical piston 2230 in a first longitudinal position and a spherical piston 2230 "in a second longitudinal position with a longitudinal central axis 2231 and a transverse central axis 2232, 2232" have. The pistons 2230 &quot;, 2230 include separate portions 2231, 2231 "having transverse central axes 2233 and 2233 &quot;, respectively. The transverse central axes 2233 and 2233" Is positioned below axes 2232 and 2232 &quot;, and transverse center axes 2233 and 2233 "are located closest to the second longitudinal position. Other configurations of the individual portions shown in Figures 80A-80E are also possible here.

84E illustrates a spherical piston 2235 in a first longitudinal position and a spherical piston 2235 "in a second longitudinal position, respectively, having a longitudinal central axis 2236 and a transverse central axis 2237, 2237" . A stepped transition 2238 of wall 2234 from wall 2239 to wall 2240.

84F shows a spherical piston 2241 in a first longitudinal position and a spherical piston 2241 "in a second longitudinal position, respectively, having a longitudinal central axis 2241 and a transverse central axis 2243, 2243 & . The piston 2241 includes discrete portions 2244 and 2244 " having respective transverse center lines 2245 and 2245 &quot;, which transverse center line extends along the transverse center axis &lt; RTI ID = (2243, 2243 ") and thus located closest to the second longitudinal position. The expansion of the toric member 2244 can be done as shown in Fig. 84A or 84B.

19690-2 (Multiple) Rotational Position and chamber  And vice versa - gearbox

Rotary piston

Figures 90a and 90b show a piston rotating around a chamber in the chamber that is always possible to react to torque induced by the piston, although it can be fixed. The enclosed space (channel) can be part of the axle, and around the center of the piston, the piston is based on Figure 11A (CT: Consumption Technology), Figure 11g (ESVT: Consumption Technology), Figure 11i (ESVT: And rotates as a piston moving on the crankshaft. The center of the axle may preferably be the same as the center of the chamber, and the axis of the connecting rod may preferably be positioned perpendicular to the axis of the axle. The connecting rod between the piston and the axle may include an enclosed space of the piston and the enclosed space may communicate with the space in the piston and the enclosed space in the axle. For example, when a spherical piston is used, there may be an extension rod connecting the channel with the sphere in the axle and may be configured similar to the rod shown in Figs. 14f and 14g, so that the length of the connecting rod And the center of the axle (Figures 90c and 90d). This depends on how the connecting rod is connected to the axle, which pressure management technique, CT and / or ESVT or the third type can be used. The CT requires a valve function, which means a sequential open / closed connection between the channel in the connecting rod and the channel in the axle. The ESVT requires an open connection between the channels.

The possibility for the construction of the joint between the connecting rod and the axle additionally depends on how the torque is transmitted from the piston to the axle via the connecting rod when the chamber can be fixed. The transmission of torque from the piston to the rotating axle through the connecting rod means that there is a fixed connection between the two components. When an ESVT pressure management system is required, the construction of the joint can be relatively simple, since the fixture (e.g., the tooth) and the corresponding groove (axle) and the connecting rod and the channel in the axle A channel through the fixture (FIG. When a CT pressure management system is required, the construction of the joint may be more complex. This may include a series and / or parallel solution of fixtures and rotating channels, wherein the openings encounter openings of the fixed channels during the portion of rotation. The serial solution includes a configuration in which the fixture and the rotating portion are located on at least two different positions on the axle, and thus on at least two joints. The parallel solution includes a configuration in which the fixture and the rotatable portion are combined in one joint.

In order to increase the torque, more than one piston can run in one chamber, and there can be sub-chambers in the chamber, for example when there is one piston per sub-chamber, Preferably in the same circular position in each sub-chamber. This can be done to simplify the construction so that the enclosed space of each connecting rod per piston is in communication with the enclosed space of the axle. The pressure in each piston is the same as that of the channel inside the other piston.

Another possibility is that more than one piston-chamber combination is combined with a x-cylinder motor (x > 1), where one or more pistons rotate within the chamber and the combination can rotate about the same center axle And the torque of each piston is transmitted to the axle so that the object, the wheel, the propeller, the lift, etc. of the motor can be performed.

rotation chamber

Figure 91a shows the chamber rotating around the piston, and although the piston can be fixed, it is always possible to react to the torque induced from the chamber. The center of the axle may preferably be the same as the center of the chamber, and the axis of the connecting rod may preferably be positioned perpendicular to the axis of the axle. The enclosed space (channel) may be part of the axle, wherein the chamber is located in the chamber (CT) of FIG. 13A, for example, FIGS. 12d, 13e, 13f, 13f, (ESVT) and Fig. 14E (ESVT: enclosed space description).

The connecting rod between the piston and the axle may include an enclosed space that communicates with the enclosed space within the axle (FIGS. 91A and 91B) and the space within the piston.

For example, when a spherical piston is used, it may be a connecting rod connecting the sphere with the channel in the axle, and may be configured as the rod shown in Figs. 14F and 14G, 90c, 90c) and the center of the piston. This configuration may be the same as the configuration of the combination in which the piston moves.

What is described in the previous chamber for the configuration of the connecting rod and axle joint when the piston moves is also applicable to the situation in which the chamber moves.

In the situation where the chamber is moving, two main solution groups may be possible, one of which is to fix the axle and the chamber rotates around the axle, where the chamber delivers torque (FIG. 92A). Another group is when the axle rotates, which can deliver the torque induced by the chamber (Figs. 92b, 92c, 93a, 93b).

When the axle rotates around the connecting rod (Fig. 91a, 91b), ESVT can be used, or CT - which depends on the possibility of constituting a valve between the enclosed space of the connecting rod and the enclosed space of the axle 91C, 91D), and no valve is possible for ESVT (FIG. 91E).

In order to increase the torque, more than one piston may be in one chamber, and sub-chambers may be present in the chamber, and when there is one piston per sub-chamber, Or may be at different circular positions, for example as shown in Figures 13a-13g, 14a-14h. Positioning at the same circular position can be performed to simplify the construction, so that the enclosed space of each connecting rod per piston is in communication with the enclosed space of the axle. The pressure in each piston is the same as the pressure inside the other piston.

As the chamber rotates, there are numerous possibilities to combine multiple solutions for all parameters.

When the chamber rotates about a bearing mounted on the axle on the chassis of the vehicle, for example, the axle rotates about the bearing mounted on the chassis and rotates in the same direction, for example, The connecting rod can be fixed between the fixed piston and the fixed axle. The axle and the chamber can additionally rotate in opposite directions. The channel in the connecting rod and axle of the combination of this solution can preferably communicate with the ESVT system (Figures 10m, 13c).

When the chamber rotates around a bearing mounted on the chassis of the vehicle, for example, and the axle is fixed on the chassis, for example, the piston is fixedly mounted on the axle to obtain the force moment required to obtain the chamber rotation And can be fixed by a connecting rod. The connecting rod and the channel in the axle of this combination of solutions are preferably in communication with the ESVT system (Figs. 91a-91c). Figures 91g-91i illustrate the corresponding solution in which the bearings of the chamber are mounted on the axle.

에, 휠, 프로펠러 등에 토크를 전달할 수 있다.
When there is more than one piston-chamber combination, wherein the chamber includes more than one piston, the chamber of the combination can deliver torque through a housing comprising, for example, at least one chamber, For example, a bare box or a car gear (box), for example Variomatic

A torque can be transmitted to a wheel, a propeller, and the like.

Each chamber of the combination may additionally be capable of transmitting its torque to axles around which the chamber extends (Figs. 93A, 93B). The axle rotates about a fixed axle, wherein the enclosed space of the stationary piston in the connecting rod communicates through a channel in the fixed axle with a pressure management system, preferably an ESVT system.

19690-2 - Preferred Example  Explanation

90A shows one rotary piston 4000 located in the vicinity of the first longitudinal position in the circular chamber 4001 and the piston 4000 is connected to the axle 4002 by the connecting rod 4003, Axle 4002 and connecting rod 4003 each include respective channels 4004 and 4005, and these channels communicate with each other. The channel 4005 is a (first) accommodation space for the piston 4000. The channel 4004 is the (second) receiving space of the piston 4000. The channel 4005 communicates with the space in the wall of the piston 4000. The central axes 3997 and 3998 are the horizontal and vertical central axes of the chamber 4001, respectively. The center point 3995 of the axes 3997 and 3998. The axle (not shown) of the axle 4002 preferably travels through the center point 3995 and is preferably positioned perpendicular to the plane through the central axis 3996 of the circular chamber 4001 . The central axis 4008 of the connecting rod 4003 preferably travels through the center point 3995. The piston 4000 'is shown in the final first circular position of the chamber 4001 and the second circular position of the piston 4000 ". The circular chamber 4001 is moved from the second longitudinal position to the first longitudinal position The piston 4000 rotates clockwise in the chamber 4001 about the center point 3995. The channel 4004 is in communication with the pressure management system, CT- and / or ESVT-system. Contra weights 3994 are located opposite the connecting rod 4003 with respect to the center point 3995. [

90B shows details of assembling the connecting rod 4003 on the axle 4002. Fig. The hub 4009 is mounted on the axle 4002 so as to be slidable in the longitudinal direction of the axle 4002 and the teeth 4007 of the axle 4002 are connected to the hub 4009 (Not shown). This configuration makes it possible to transmit torque from the connecting rod 4003 to the axle 4002. [ This configuration is a channel 4006 'in the wall of the hub 4009 with the channel (first accommodation space) 4005 in the connecting rod 4003 and the channel (second accommodation space) 4004 in the axle 4002. [ ) And the channel 4006 of the channel. The central axis 4008 is the central axis of the channels 4005, 4006 and 4006 ', respectively, and is also the longitudinal central axis of the connecting rod 4003. The center axis 4008 is positioned perpendicular to the center axis (not shown) of the axle 4002. The connecting rod 4003 is mounted on the hub 4009. A connecting rod 4003 having a center rod 4010 and a reinforcing pin 4011 in which a receiving space 4005 is disposed is illustrated and a connecting rod 4003 is disposed on the hub 4009 between the reinforcing pins A bolt 4016 for mounting is disposed. Washers 4012 and spring washers 4013. The end 4017 of the center rod 4010 is disposed within the recess 4015 of the hub 4009. A seal 4018 between the end 4017 and the recess 4015. The contra weight 3994 is shown as part of the hub 4009.

90C shows an extension rod 4020 of the connecting rod 4003 on which the piston 4000 is mounted. The piston 4000 is shown as being located near the first circular position 4021. And the remaining parts are the same as those shown in Fig. 14F. The connecting rod 4003 includes an extension rod 4020 which extends into the axle 4002 in the end 4023 of the channel 4005 of the connecting rod 4003 and to the axle 4002 Rings 4021 and 4022 so as to compensate for the variable distance of the wall 4024 of the piston 4000 to the axle 4002. [ The extension rod 4020 has a channel 4025 which communicates with the space 4026 of the piston 4000 through the channel 4005 and the channel 4027 of the connecting rod 4003. The distance l between the intersection point 3990 'between the central axis 4008 of the connecting rod 4003 and the central axis 3996 of the chamber 4001 and the end 3991 of the extension rod 4020.

90D shows the extension rod 4020 of the connecting rod 4003 when the piston 4000 is located in the second circular position 4028 on which a piston 4000 " is mounted and shown. The point of intersection between the central axis 4008 of the connecting rod 4003 and the central axis 3996 of the chamber 4001 and the point of intersection between the central axis 4009 of the connecting rod 4003 and the central axis 3996 of the chamber 4001 are the same as those shown in Figures 14G and 90C, The distance l 'between the ends 3991. The length l'<1 (shown in FIG. 90C).

90E shows the configuration of Fig. 90A in communication with the CT-pressure management system based on Fig. 11A, which is now configured in a plane through the central axis 4029 of the axle 4002. Fig. The joint 4051 between the axle 4002 and the connecting rod 4003 in Figs. 90A and 90B is as shown in Fig. 11D. The channel 4005 of the connecting rod 4002 communicates with the channel 4004 of the axle 4002. The last described channel 4004 communicates with channels 822 and 823, respectively. Reference is made to Figs. 11A and 11D for the description of other reference numerals in the drawings.

Figure 90f shows the joint 4052 according to Figure 11t for the transition of the axle 4002 including the channel 4004 with the channel 4005 of the connecting rod 4002 of Figures 90a and 90b and the ESVT - a pressure management system. Reference is made to Figs. 11G and 11T for the description of other reference numerals in the drawings.

Figure 90g shows a joint 4052 including a connecting rod 4003 including a channel 4005 and a joint 4002 according to Figure 11t for an axle 4002 including a channel 4004 as shown in Figures 90a and 90b. Lt; RTI ID = 0.0 &gt; 11i. &Lt; / RTI &gt; Reference is made to Figs. 11I and 11T for other reference numerals in the above drawings.

Figure 90h shows the ESVT-pressure management system based on Figure 90g at the combination of the camshaft 4060 controlling the timing of the ESVT system of Figure 11i and shows the ESVT-pressure management system based on H ₂ derived from the electrolysis of H ₂ O according to Figure 11q The energy is introduced from the combustion motor 4061 driven by the combustion motor 4061. Reference is made to Figures 90g, 11i, 11t and 11q for the description of other reference numerals in the drawings and other details.

901 shows four rotating pistons (5070, 5071, 5072, 5073, respectively) in a circular chamber 5074, which includes four sub chambers 5075, 5076, 5077, 5078, one for each piston, The circular chamber 5074 is preferably fixed. The rotation pistons 5070, 5071, 5072 and 5073 are respectively located in the same circular positions within each of the sub-chambers 5074, 5075, 5076 and 5077, and the circulation of the pistons is controlled by the center point of the circular chamber 5074 5079 in a clockwise direction. Each of the pistons 5070, 5071, 5072 and 5073 rotates about the same axle 5085, and its center is the same as the center point 5079. Each of the pistons 5070, 5071, 5072 and 5073 is supported by connecting rods 5080, 5081, 5082 and 5083 including extension rods 5090, 5091, 5092 and 5093 as described in Figures 90c and 90d, And is connected to the axle 5085. In fact, this configuration for the pistons 5070, 5071, 5072, 5073, connecting rods 5080, 5081, 5082, 5083 and extension rods 5090, 5091, 5092, 5093 is shown in Figs. 90A and 90B There is a 4x configuration. All four connecting rods 5090, 5091, 5092 and 5093 are bolted to a common hub 4029. The hub 4029 is mounted on the axle 5085 by means of a tooth 4007 of the axle 5085 which is fitted into a corresponding groove 4007 ' of the hub 4029, Respectively.

90j shows an enlarged view of the assembly of the axle 5085 and connecting rods 5080, 5081, 5082, 5083 of Fig. 90i. In fact, this joint is a four-double of the joint shown in Figure 90b in four equal circle segments over 360 [deg.]. Common hub 4053. The channels 5086, 5087, 5088, 5089 of each connecting rod 5080, 5081, 5082, 5083 are in constant communication with the channel 5090 in the axle 5085 and thus communicate with each other. This allows direct communication between the channel 5090 in the axle 5085 and the space within each piston 5070, 5071, 5072, 5073 (not shown here - see Figures 90c and 90d) The configuration preferably functions with an ESVT-pressure management system.

Fig. 90K illustrates the relationship between the configuration of Figs. 90i and 90j in communication with the ESVT-pressure management system according to Fig. 11i and the central hub 4053 of the axle 4052 of Fig. 11t based on the combination of the common hub 4053 of Fig. Lt; RTI ID = 0.0 &gt; 4054 &lt; / RTI &gt; Reference is made to Fig. 11t for a description of the part of the joint.

Figure 90l shows a preferred embodiment of a motor based on the configuration of the joint 4054 shown in Figure 90k in combination with a camshaft 5060 controlling the timing of the ESVT system, Is introduced from a combustion motor 4061 which is driven by H ₂ derived from the electrolysis of H ₂ O or electrical energy from the combustion chamber 832. Reference is made to Figures 90K and 11Q for the description of other reference numerals in the drawings.

Figure 91a shows one circular chamber 4030 (over 360 °) that is rotated counterclockwise about the axle 4032 and suspended by the three spokes 4034. The spokes 4034 are shown in cross-section different from the cross-section of the connecting rod 4033. The piston 4031 is located in the vicinity of the first circular position in the circular chamber 4030. The piston 4031 is preferably fixed by a connecting rod 4033 and the hub 4038 which is the last mentioned suspension part includes a tooth part for taking a reaction force from the circular chamber 4030 on the piston 4031, And is fixedly mounted on the axle 4032 by a groove (see Fig. 91B). Between the hub 4035 of the spokes 4034 and the axle 4032 there is a bearing 4039 which is fixed on the hub 4035 of the spoke 4034 by a suitable fastener, Thereby allowing the hub 4035 of the axle 4032 to rotate about the axle 4032. A belt 874 rotating near the edge of the chamber housing 4036 extends along the direction of rotation of the chamber 4030.

91B shows details of assembly of the connecting rod 4033 and the axle 4032. Fig. The hub 4035 of the spokes 4034 includes a bearing 4039 which is appropriately rotationally fastened with the rotating hub 4035 of the spokes 4034. No valve features are arranged here because the bearing 4039 includes the walls of the upper portion 4038-1 of the hub 4038 and the walls 4044 and 4045 of the wall of the axle 4032 Because it belongs to a different cross section. The hub 4038 of the connecting rod 4033 includes two portions that are the upper portion 4038-1 and the lower portion 4038-2 that are connected to the connecting rod 4033. The top and bottom portions are bolted together by a bolt 4040 that further bolts the connecting rod 4033 to the hub 4038. The hub 4038 includes a groove 4007 'that is fitted in the tooth 4007. The channel 4044 through the channel 4044 of the wall of the axle 4032 and the channel 4045 through the wall of the upper portion of the upper portion 4038-1 of the hub 4038 and the channel 4046 through the connecting rod 4034, There is as much constant communication as possible between the channels 4043 of the axle 4032 into the interior of the vehicle. The channels through the extension rods are not shown, see Figures 90c and 90d. Due to constant communication, the use of an ESVT system is particularly desirable when more than one chamber is applied on one axle, and the use of a CT system is optional.

All solutions for combination with CT- and / or ESVT pressure management in accordance with the embodiment of Figures 90A-90D can be applied to the embodiment of Figures 91A and 91B.

A chamber having four sub-chambers not shown and merely illustrative only includes four pistons based on the configuration shown in Figures 91A and 91B. The chamber rotates about an axle, and the central axis of the axle travels through the center point of the centerline of the circular chamber. The space within each piston is constantly interlocked through the channels (accommodation spaces) in each of the four extension and connecting rods having the channels in the axle, and this configuration preferably functions with the ESVT system.

Fig. 91C shows a configuration which is comparable to Fig. 91B, in which the bearing 5100 includes a portion of the hub 5101 for assembling the connecting rod 5102 to the axle 5103 and a portion of the hub 5101 having the axle 5103 5106) (see FIG. 91D) and the hub 5104 connecting the spokes 5105 are different. And the channel 5109 of the wall of the axle 5103 is now located in the portion of the axle 5103 where the bearing 5100 is located. The section KL is a section through the hub 5101 of the axle 5103 and the connecting rod 5102 wherein the axle 5103 is connected to the hub 5104 by a toothed portion 5107, As shown in FIG. The section NM is a section through axle 5103 and hub 5106 of spoke 5105 (see FIG. 91d), wherein hub 5106 is rotated about axle 5103 by bearing 5100 can do.

FIG. 91D shows cross sections NM and KL of FIG. 90C. In addition, a cross-section of the chamber 5110 is shown and the wall 5111 of the chamber 5110 has a larger opening 5113 for the connecting rod 5102 and an extension rod (not shown here - 90d). &Lt; / RTI &gt; The engagement of the bearing 5100 with the hub 5101 of the connecting rod 5102 is such that the bearing 5100 can rotate within the hub 5100 of the connecting rod 5102 while rotation is transmitted to the hub 5106 of the spoke 5105, It can not be done within. The engagement of the axle 5103 with the bearing 5100 is such that the bearing can rotate around the axle 5102. The result is that the chamber 5110 does not have a constant communication with the channel 5114 of the axle 5103 as it rotates about the axle 5103, and a -CT pressure management system can be used here. There is a preferred embodiment of the rest of the motor shown earlier in Figures 90e (CT), 90h-90h (inclusive) (ESVT) with the embodiment shown in Figures 91a-91d (inclusive).

91E shows the connection of the channel 4034 of the axle 4032 and the channel 4035 of the connecting rod where a constant communication is possible between the channels 4035 and 4034. The bearing 4039 rotates with the connecting rod 4033 at the same rotational speed so that the channel 4037 always communicates with the channel 4035 of the connecting rod 4033. The central axis 4036 of the connecting rod 4033. The axle 4040 includes an additional channel 4041. The channel 4041 is in constant communication with the channel 4032 of the axle 4040 through the channel 4042. The channel 4041 is in constant communication with the channel 4037 of the bearing 4039 through the channel 4045 of the upper hub 4038-1. The portion 4046 of the axle 4040 has a reduced diameter about the channel 4042 in the wall of the portion 4046. [ The channel 4035 of the connecting rod 4035 is in constant communication with the piston 4031 according to Figures 90c and 90d (a spherical piston is used). The channel 4034 of the axle 4032 communicates with the pressure management system. ESVT (enclosure volume technology) can work well with this configuration.

For a valve used in a joint of a connecting rod and an axle, refer to FIG. 11D, which is derived therefrom when using CT (consumable technology), for example, shown in FIG. 90D (reference numeral 4051). For ESVT ¹ , refer to FIG. 11t, which is derived therefrom and is shown, for example, in FIG. 90f (reference numeral 4052) and in FIG. 90k (reference numeral 4054).

The engagement between the upper hub 4038-1 and the lower hub 4038-2 and the bearing 4039 is such that the bearing is not movable relative to the hub portions 4038-1 and 4038-2. This ensures that the channel 4037 in the wall of the bearing 4038-1 is always in communication with the channel 4045 in the wall of the upper hub 4038-1 and therefore the channel 4035 of the connecting rod 4033 and the channel 4035 of the axle 4032 are present. The use of the ESVT system may be possible.

If the bearing 4039 has a sliding engagement with the hub 4038-1 / 4038-2, e.g., a press fit engagement with the axle 4040, the communication will cause the hub 4038 to rotate about the axle When it stops. The use of a CT system may be possible.

92A schematically shows a three-cylinder motor 4090 in which a piston 4091 moves in a circular chamber 4092 and the circular chambers are identical and have a central axis 5000 and a main motor axle 4094 The chambers 4092 are interconnected by a housing 4095 and the gearbox 4093 is secured to the assembly 4093 by bolts 4096, a spring 4097 and a washer 4098. [ . The main motor axle 4094 of the motor 4090 is in direct communication with the axle 5004 of the gear box 4093. The gear box 4093 includes a drive shaft axle 5000. The gear box 4093 is integrated in the reverse direction. Although not shown, as an alternative, a clutch can be inserted between the axle 5004 and the main motor axle 4094, wherein when the clutch is pressed on a wheel (not shown), for example, a flywheel) The axle 4094 communicates with the axle 5004 of the gear box 4093 via the clutch and the axle 5004 of the gearbox constantly communicates with the main motor axle 4094. The motor 4090 rotates freely on the axle 5004 of the gear box 4093 and thereby freely rotates on the output axle 4099 of the gear box 4093 when the clutch is not pressed on the flywheel . A pressure management system 5001, preferably an ESVT system, communicates with the channel 5002, which communicates with the receiving space 5003 of each piston 4091 and communicates with the interior 5006 of each piston. A bolt 5004 (with a spring and a washer) mounts two chamber portions 4092-1 and 4092-2 together for each chamber 4092. The piston 4091 transmits its torque to the main motor axle 4094, for example, according to Figs. 90A to 90C, or, according to Figs. 90I and 90J, by a hub 5005.

92B schematically illustrates a three-cylinder motor 5010, wherein the piston 5011 moves within a circular chamber 5012. [ The chambers 5012 are the same and are positioned parallel to each other around the main motor axle 5013. The housing plate 5017 holds the chamber 5012 together. The torque generated by the piston 5011 is transmitted to the connecting rod 50xx by the hub 5019 in accordance with, for example, Figs. 90A to 90C, or according to Figs. 90I and 90J or according to Figs. 91A to 91D. To the main motor axle 5013 via the main motor shaft 5013. On each side of the main motor axle 5013 there is an assembled variable pitch wheel 5014 which is connected by a bolt 5021 to the opposing wheel 5015 on the wheel axle 5016 of the vehicle, 5010 are shown at a high pitch and a low pitch is shown on the side of the wheel axle 5016 (the vehicle moves quickly). The distance x shows that this distance remains unchanged when the pitch of the wheels 5014 and 5015 changes - the change can be at any pitch between the high pitch and the low pitch. The channel 5019 in the center of the main motor is in direct communication with the pressure management system 5020, preferably the ESVT-system. The opposite arrangement is not shown, so the vehicle can move forward and backward.

92C shows the same bar as in Fig. 92B, wherein the pitch of the wheel 5014 'on the side of the motor 5010 is small and there is a high pitch of the wheel 5015' on the side of the wheel axle 5016 (Fig. The vehicle moves slowly).

FIG. 93A schematically shows a three-cylinder motor 5020, and the chamber 5021 rotates about the central axle 5022. The chamber 5021 is connected to the central axle 5022 by corner brackets 5023 and 5023 'on each side of the chamber 5021 so that the torque generated by the chamber 5021 is transmitted to the corner bracket Is transmitted to the central axle 5022 through the hub 5034 outside the respective hub 5034 of each piston 5025 where the central axle 5022 is connected to each other by only the brackets 5023 and 5023 ' 5022 ', and includes a bearing 5033 that includes a portion 5033' that corresponds to a portion of the central axis 5022. The hub 5034 is mounted on the inner axle 5032. The center axle 5022 is in communication with the external gear box 5024 through a gear wheel 5028. The gear wheel communicates with the gear wheel 5029. The gear wheel 5029 indirectly communicates with the drive shaft axle 5030. Rotation direction 5031 of drive shaft axle 5030. Each chamber 5021 includes a piston 5025 and a ring 5026, which function as a flywheel, which is located furthest away from the central axis 5022. The piston 5025 is assembled to the inner axle 5032 by a hub 5034. The inner axle 5032 is mounted to the vehicle and the gear box by fasteners 5035 and 5035 ', respectively. A bearing 5033 is provided between the inner axle 5032 and the axle 5022 (see also the enlarged view). Pressure management system 5027, preferably an ESVT-system. Communicating 5036 with the channel 5037 in the inner axle 5032 of the pressure management system 5027. The channel 5037 communicates with a channel 5039 in a connecting rod 5040 (shown schematically) that communicates with a space 5038 in the piston 5025.

93B shows an enlarged view (4: 1) of the left corner of the bearing 5033 and the center shaft 5022 between the center axle 5022 and the inner axle 5032. Fig. Fastener (5035).

207 Preferred Example  Explanation

Figure 100 shows a so-called indicatior diagram. This figure schematically shows the adiabatic relationship between the pump stroke volume (V) and the pressure (p) of a typical single-stage one-way working piston pump with a cylinder of fixed diameter. The increase in operating force applied per stroke can be read directly from the figure and is a quadratic equation of cylinder diameter. The pressure p and thus the actuating force F generally increase during stroke until the valve of the body to be inflated is opened.

Figure 102a shows a diagram of the pressure applied to the piston pump according to the present invention. This shows that the diagram for pressure p is similar to that of a conventional pump, but the actuation force is different and is entirely dependent on the selected cross-sectional area of the pressurization chamber. This entirely depends entirely on, for example, the operating force not exceeding a predetermined maximum or the magnitude of the operating force fluctuating according to ergonomic requirements. This is particularly required in the case where the water pump is merely delivering the medium without significant change in pressure, as in the case of a water pump, for example. The shape of the longitudinal and / or transverse cross-section of the pressure chamber may be any kind of curve and / or line. It is also possible that the cross-section is increased by, for example, increasing pressure (Fig. 102 (b)). One example of operating force is the dotted thick line (1 or 2). The various wall possibilities marked 1 and 2 correspond to the abovementioned lines 1 and 2 of the figure. The A-section relates to the pump in which only the piston moves, and the B-section relates to the pump in which only the chamber moves. A combination of both movements is possible at the same time.

102b shows an example of an acupressure diagram of a piston pump with a chamber having a cross section that increases with increasing pressure.

Figs. 103A, 103B, 103C and 103D show details of the first embodiment. The piston moves in a pressurized chamber comprising a cylindrical and conical portion with a circular cross section with a decreasing diameter when the gas and / or liquid medium increases. This is based on the specification that the operating force should not exceed a predetermined maximum value. Transitions between the various diameters are gradual without discontinuous steps. This means that the piston can easily slide in the chamber and can adapt itself to the area and / or shape of the varying cross-section without losing the sealing function. If the operating force has to be lowered by the increasing pressure, the cross-sectional area of the piston decreases, whereby the length of the circumference also decreases. The circumferential length reduction is based on compression or relaxation up to the buckling level. The longitudinal section of the piston means is trapezoidal with a wall of the pressure chamber and a variable angle (?) Of, for example, less than 40 degrees, so that it can not be deflected backward. The dimensions of the seal mean a change in three dimensions during each stroke. The support portion of the piston means, for example the disk or integrated rib of the sealing means, for example, located on the non-press side during the pumping stroke of the piston, protects against deflection under pressure. The loading portion of the piston means, e. G., A spring washer having a plurality of segments, may also be mounted, for example, on the pressurized side of the piston. This squeezes the flexible seal towards the wall. This is convenient when the pump is not used for a predetermined time and the piston means is folded for a predetermined time. By moving the piston rod, the sides of the trapezoidal section of the sealing portion of the piston means are propelled axially and radially, so that the sealing edge of the piston follows the decreasing diameter of the pressure chamber. At the end of the stroke, the bottom of the chamber at the center becomes higher to reduce the volume of unused space. The piston rod is guided mainly in the cap, which is locked with the pressure chamber. When the piston is sealed to the wall of the chamber in both directions of its movement, the piston rod includes an inlet channel having a spring-actuated valve that is closed, for example in the event of overpressure in the chamber. Without the use of the loading portion of the piston means, this separate valve can be redundant. In the pump design according to the invention, the portion of the pump is optimized for operating force. The inner diameter of the pump extends over most of the length of the pump chamber which is larger than that of the conventional pump. As a result, even if the volume of the remaining portion of the chamber is lower than that of the conventional pump, the inlet volume is higher. This ensures that the pump can pump faster than the existing pump, the required maximum operating force is significantly reduced, and is lower than the level reported by the consumer as optimal. The length of the chamber is reduced, so the pump can be practical for women and teenagers as well. The volume of the stroke is still higher than that of the conventional pump.

Figure 103a shows a piston pump with a pressurizing chamber 1 having parts of the various sections of its cross section of the wall sections 2,3,5 and 5. Piston rod (6). The cap (7) stops the piston means and guides the piston rod (6). Transition sections (16, 17, 18) between sections with walls (2, 3, 4, 5). The longitudinal center axis (19) of the chamber (1). Piston 20 at the beginning and piston 20 'at the end of the pump stroke.

Figure 103b shows the support part 10 of the piston means attached to the piston rod 6 between the elastic material and the loading part 9, for example two parts of the locking means 11, and the segments 9.1, 9.3) (the other segment is not shown). The piston rod (6) has an inlet (12) and a valve (13). The angle between the pressure chamber (1) wall (2) and the sealing portion 8 of the piston means (α _1). Sealing edge (37). Distance a is the distance from the sealing edge 37 to the center axis of the chamber 1 in the transverse section at the beginning of the stroke.

Figure 103 (c) shows the outlet channel 14 of the means 15 for reducing the volume of unused space. The angle? ₂ between the wall 5 of the pressure chamber 1 and the sealing portion 8 'of the piston means. The distance a 'is the distance from the sealing edge 37 to the center axis of the chamber 1 in the transverse section at the end of the stroke. The distance a 'is approximately 41% of the distance a. Loading portion 9 '.

_inside 60 - 19.3 mm, 길이 500 mm)의 챔버의 종방향 단면을 도시하고 있다. 또한, 다른 힘 크기도 선택될 수 있다. 이는 단지 일정한 작동력이 인체공학적으로 정확하지 않을 수 있을 때 본 발명에 따른 플로어펌프의 정량화를 위한 시작 지점을 제공한다. 비교로서, 기존 저압 플로어 펌프(

_inside 32 mm, 길이 470 mm)는 점선으로 도시되며, 기존 고압 플로어 펌프(

_inside 27 mm, 길이 550 mm)의 것은 점선으로 도시되어 있다. 본 발명에 따른 플로어 펌프 양자 모두는 더 큰 스트로크 체적을 가지며, 따라서, 더 신속히 팽창하는 타이어 및 기존 펌프보다 더 낮은 작동력을 갖는다는 것을 명료히 보여준다. 본 발명에 따른 챔버는 전체 스트로크 동안의 인체공학적 요구에 맞춤화될 수 있다.
Figure 103d shows a floor pump according to the present invention in which its cross-section is selected such that its operating force remains substantially constant and is selected for example according to ergonomic requirements at 277N,

_inside 60 to 19.3 mm, length 500 mm). Other power magnitudes can also be selected. This provides a starting point for the quantification of the floor pump according to the invention when only a certain operating force may not be ergonomically correct. As a comparison, a conventional low pressure floor pump (

_inside 32 mm, length 470 mm) are shown in dashed lines and conventional high pressure floor pumps

_inside 27 mm, length 550 mm) is shown by a dotted line. Both of the floor pumps according to the present invention clearly show that they have a larger stroke volume and therefore have a lower operating force than a tire and a conventional pump that expand more rapidly. The chamber according to the invention can be tailored to ergonomic requirements during the entire stroke.

Figs. 104A, 104B, 104C, 104D, 104E and 104F show the details of the second preferred embodiment. The sealing portion of the piston means consists of an elastically deformable material supported by a support means that is rotatable about an axis parallel to the central axis of the chamber. The result of these movements is to support a larger area of the sealing means, with a higher pressure being in the chamber. The loading portion for the support portion initiates movement of the support means. The flat-shaped loading portion of the spring shape can change the dimension in a direction perpendicular to the centerline of the chamber. The spring becomes more rigid, and the pressure in the chamber becomes higher. It may also be a spring on an axis for rotating the support means. By reducing the diameter of the sealing portion, it increases its length. This is the case, for example, with elastically deformable material which can only be somewhat compressive, such as rubber. Thus, the piston rod is secured to the outside of the sealing means at the beginning of the stroke. If another material is selected for the sealing portion, its length can be kept constant or reduced by reducing its diameter.

FIG. 104A shows a piston pump with a pressure chamber 21 having portions of various cross-sectional areas. The chamber has a cooling rib 22 on the high pressure side. The chamber can be (injection) molded. Piston rod (23). The cap 24 guides the piston rod. The piston 36 at the beginning and the piston 36 'at the end of the pump stroke.

104B shows an elastically deformable sealing portion 25 fastened to the piston rod 23 by means 26 (not shown). A portion (27) of the piston rod (23) is secured to the outside of the sealing portion (25). The support portion 28 is caught on the ring 29 fastened to the piston rod 23. The support portion 28 can rotate about the axis 30. The loading portion 31 includes a spring which is fastened in the hole 32 onto the piston rod 23. Sealing edge (38).

Figure 104 (c) shows that the portion 27 of the piston rod 23 is now substantially covered by the elastically deformed sealing means 25 'whose length is increased and whose diameter is reduced. Sealing edge 38 '. The distance a 'between the central axis 19 of the chamber and the sealing edge 38 is about 40% of that of the distance a in the illustrated cross-section.

Figure 104d shows a section AA of Figure 104b. The loading portion 31 is fastened at one end within the bore 32 of the piston rod 23. Support portion 28 and ring 29. The support portion is stopped by the stop surface 33 (not shown). The support portion 28 is guided by guide means 34 (not shown).

Fig. 104E shows a cross section BB of Fig. 104C. The support means 28 and the loading means 31 are moved toward the piston rod 23. The ribs 22.

Fig. 104f shows an alternative for the loading means 31. Fig. Which includes a spring 35 on each axis 30. [

105A, 105B, 105C, 105D, 105E, 105F, 105G, and 105H show the details of the third embodiment. This is a modification of the first embodiment. The seal includes a flexible impermeable membrane for gas and / or liquid media. This material can change its dimensions in three directions without folding. This seal is mounted in an O-ring sealing against the wall of the chamber. The O-ring is loaded on the wall by a loading means, for example a spring in the circumference. The O-ring and the spring are further supported by a support means that is rotatable about an axle engaged with the piston rod. This support means can be loaded by a spring.

Figure 105a shows a longitudinal section of a piston pump similar to that of Figure 103a. The piston 49 is at the start and end of the pump stroke 49 '.

Figure 105b shows the piston means at the beginning of the stroke including the sealing means 41, for example the sealing means 40 fastened to the O-ring, for example a stressed skin. This O-ring is loaded by a spring 42 which is located on the circumference of the sealing means 41 and the sealing means 40. There is a central axis 39 of the spring 42. The O-ring and / or spring 42 is supported by a support means 43 which is attached to the piston rod 45 and is rotatable on an axis 44 which is positioned perpendicular to the central axis 19. This includes a specific amount of individual member 43 'loaded during compression during (compression) pump stroke. They are located around the circumference of the sealing means (40, 41) and loading means (42) they support. The support means 43 can be loaded by a spring 46. There is an angle beta ₁ between the wall of the chamber 2 and the support means 43. [ The piston rod 45 does not have an inlet or a valve. The support ring and / or the loading ring in the form of a spring can be mounted in the O-ring as an alternative to the spring 42 (not shown). Sealing edge (48).

Figure 105c shows the piston means at the end of the stroke. The sealing means 40 ', 41' are thicker than the ones 40, 41 at the start of the stroke. Spring 46 '. There is an angle [beta] ₂ between the wall 5 and the support means 43 at the end of the stroke. The distance a 'between the sealing edge 48 and the center axis 19 of the chamber is approximately 22% of the distance a at the start of the stroke in the section shown. A smaller distance, for example 15%, 10% or 5%, is possible and depends only on the configuration of the suspension of the piston on the piston rod. Thus, this is also valid for all other embodiments.

Figure 105d shows a cross section CC of Figure 105a with the support means 43, the axle 44 and the bracket 47. Fig.

FIG. 105E shows the cross section DD from FIG. 105A.

Figure 105f shows two positions of the piston 118 of Figure 105g and 118 'of Figure 105h in the chamber.

Figure 105g shows a piston made of composite material. The piston includes an elastic impermeable material and a skin of the fiber (111). The fiber architecture creates a dome shape when under internal pressure. This stabilizes the piston movement. Alternatively, the sealing means may comprise a liner, a fiber and a cover (not shown). If the liner is not airtight, an impermeable skin may be added (not shown). All materials on the compression side of the piston conform to the specific environmental requirements of the chamber. The skin is mounted in the seal 112. Within the skin and seal, a spring force ring 113 can be mounted, which can be resiliently deformed in its plane and improves the loading of the ring 114. Sealing edge (117).

Figure 105h shows the piston of Figure 105g at the end of the pump stroke. The dome is still compressed to shape 115 if there is a maximum overpressure. The shape 110 'is the result after the overpressure is reduced, for example, after the medium is discharged.

Figs. 106A, 106B and 106C show the details of the fourth embodiment. The piston means includes, for example, a rubber tube having a reinforcing portion in the form of a fabric yarn or cord wound around it. The neutral angle (= so-called braid angle) between the tangent of the reinforcement winding and the center line of the hose is calculated to be mathematically 54 ° 44 '. The hose under internal pressure will not change the dimensions (length, diameter) assuming no stretching of the reinforcement. In this embodiment, the diameter of the piston means decreases with respect to the decreasing diameter of the cross section of the chamber at increasing pressure. Braid angles should be wider than neutral. The shape of the main part of the longitudinal section of the compression chamber is substantially conical due to the behavior of the piston means. At the end of the pump stroke, when the compression medium is removed from the chamber, the piston means increases its diameter and its length is reduced. Increasing the diameter is not a practical problem. The sealing force from the piston to the wall of the compression chamber must be increased by increasing the pressure. This can be done, for example, by selection of the angle of the bracket so that the piston diameter is slightly less than the reduction in diameter of the cross-section of the chamber. Thus, the braided angle can also be selected to be smaller and / or neutral than neutral. In general, the selection of the braid angle depends entirely on the design specification, so that the braid angle may be wider and / or smaller and / or neutral. It is even possible to change the braid angle from place to place in the piston. Another possibility is that a plurality of reinforcement layers in the same cross section of the piston are present with the same and / or different braze angles. Any type of reinforcement material and / or reinforcement pattern may be used. The location of the stiffening layer (s) may be at any position in the longitudinal section of the piston. The amount of lining and / or cover may be more than one. It is also possible that there is no cover. The piston means may also include loading and supporting means, such as those described above. In order to make it possible to accommodate the larger changes in the area of the cross section of the chamber, slightly different configurations of the piston means are required. The cone now includes fibers under tension. They are wound together at the top of the cone near the piston rod and at the open side of the cone at the bottom of the piston rod. They can also be fastened to the piston rod itself. The pattern of fibers is designed, for example, to be in the chamber of the pump where they are under higher tension and higher pressure is compressed by the medium. Other patterns are of course possible only according to the specifications. They deform the skin of the cone and adapt itself to the cross-section of the chamber. The fibers can be loosely laid on the liner or loosely in the channel between the liner and the cover, and these fibers can be integrated on one or both of the two. It is necessary to have a loading means to obtain a proper seal against the wall if no pressure is present yet below the cone. A loading member, for example a spring force member in the form of a ring, plate or the like, can be configured in the skin, for example, by inserting in a molding process. The suspension of the cone on the piston rod is better than that of the above embodiment because the piston will now be loaded by tension. Thus, more balanced and less material is required. The skins and covers of the pistons can be made of an elastically deformable material that conforms to certain environmental conditions, while the fibers are elastic or rigid and can be made of any suitable material.

106a shows a longitudinal cross-sectional view of a pump having a chamber 60. Fig. The wall portions 61, 62, 63, 64, 65 are cylindrical shapes 61, 65 and conical shapes 62, 63, 64. There are transitions 66, 67, 68 and 69 between the parts. There is a piston 59 at the beginning of the pump stroke and a piston 59 'at the end of the pump stroke.

Fig. 106 (b) shows a hose having the piston means 50 and the reinforcing portion 51. Fig. The hose is fastened to the piston rod 6 by a clamp 52 or the like. The piston (6) has ribs (56, 57). The ribs 56 prevent the movement of the piston means 50 relative to the piston rod 6 towards the cap 7 while the ribs 57 prevent the piston 7 against the piston rod 6, Thereby preventing movement of the means 50. Other configurations of fittings may be possible (not shown). Outside the hose, the projection 53 seals against the wall 61 of the chamber 60. In addition to the reinforcement 51, the hose includes a lining 55. As an example, a cover 54 is also shown. The shape of the longitudinal section of the piston means is an example. Sealing edge (58).

Figure 106c shows the piston means at the end of the stroke, where the gas and / or liquid medium is under pressure. The piston means can be designed in such a way that the diameter variation occurs only through a radial change (not shown).

Figure 106d shows the piston 189 of Figure 106e and the piston 189 'of Figure 106f at the beginning and end of the pump stroke of the chamber of Figure 106a, respectively.

FIG. 106E shows a piston means having a general shape of an approximate cone having a top angle ₂ ? ₁ . This piston means is shown when there is no overpressure on the side of the chamber. The piston means is mounted on top of the piston rod 180. The cone is open on the compression side of the piston. The cover 181 includes a sealing portion shown as a projection 182 having a sealing edge 188 and an inserted spring force member 183 and a fiber 184 and a liner 185 as support means. The member 183 provides loading on the cover such that the projection 182 seals the chamber wall if there is no overpressure on the side of the chamber. The fibers 184 may be located within the channels 186 and these fibers are shown positioned between the cover 181 and the liner 185. The liner 185 may be impermeable - if not impervious, an individual layer 209 (not shown) is mounted on the liner 185 at the compression side. The fibers are mounted to the piston rod 180 and / or to each other within the upper portion 187 of the cone. The same applies also to the bottom end of the piston rod 180.

Figure 106f shows the piston means at the end of the stroke. The incidence is now 2ε _2, is approximately 44% of the center axis of the chamber (19) and the sealing edge 188 distance (a ') is now the distance at the beginning of the stroke in the shown cross-section (a) between.

Figures 107a, 107b, 107c, 107d and 107e illustrate a fifth embodiment of a pump with a piston constructed as another composite structure comprising a base material which is highly elastic in all three dimensions with very high relaxation In detail. If it is not self-sealing, it can be made air-tight with, for example, a flexible membrane on the compressed side of the piston means. The axial stiffness is achieved by a multiplicity of integral stiffeners lying in the transverse section in a pattern that optimally fills this section, while the smaller the diameter of the transverse section sections, the smaller the distance therebetween, Which means that the pressure in the compression chamber is higher. The higher the pressure rate, the more the angles are reduced and closer to the axial direction. Now, therefore, the forces are transmitted to the washer connected to the support means, for example the piston rod. The piston means can be mass produced and low cost. The sealing means, in the form of rigid, if necessary flexible, membrane, may be injection molded with the base material in one operation. For example, the stiffeners can be joined together at the top, which makes handling easier. It is also possible to manufacture the membrane by 'burning' it in the base material during or after injection molding. It is particularly convenient if the base material is thermoplastic. The hinges should not be 'burned'.

Figures 107f, 107g, 107h, 107i, 107j, 107k, 107l, 107m illustrate an embodiment of a chamber and a sixth embodiment of a piston fitted in this chamber. The sixth embodiment of the piston is a modification of one of Figs. 107A, 107B, 107C, 107D and 107E. If the change in the area of the cross section of the piston and / or the chamber between the two positions in the direction of movement is continuous but still too large to cause leakage, it is advantageous to minimize changes in other parameters of the cross section. This can be illustrated, for example, using a circular cross section (fixed shape), where the circumference of the circle is? D, while the area of the circle is?? D ² (D = circle diameter). That is, the reduction of D will only provide a linear reduction of the circumference and a squared reduction of the area. It is also possible to maintain the circumference and reduce only the area. For example, if the shape of the circle is also fixed, there is a certain minimum area. An advanced numerical computation, in which the shape is a parameter, can be done using the Fourier series extensions mentioned below. The cross-section of the compression chamber and / or the piston may have any shape, which may be defined by at least one curve. The curve is closed and can be roughly defined by two intrinsic modular parametrized Fourier series extensions, one for each coordinate function.

here,

c _p = cos-weighted mean value of f (x)

The sin-weighted mean value of d _p = f (x)

p = expression of triangular alignment

107f and 107k show examples of the above curves by using different sets of parameters in the following equations. In these examples, only two parameters are used. If more coefficients are used, for example because the curved transition has a maximum value for the specific maximum radius and / or for the tension in the seal that may not exceed a certain maximum value, for example under a given premise, It is possible to find optimized curves that comply with critical needs. By way of example, Figures 1071 and 107m show optimized convex and convex curves to be used for possible variations of the bordered domains in a plane under the constraint that the length of the boundary curve is fixed and the numerical curvature is minimized. It is possible to consider the minimum possible curvature for a particular desired target area by using the starting area and the starting boundary length.

The piston shown in the longitudinal section of the chamber is shown primarily for the case where the boundary curve of the cross section is circular. That is, the shape of the longitudinal cross section of the piston may differ, for example, when the chamber has a transverse cross section according to this non-circular shape, for example, in Figures 107f, 107k, 107l, 107m.

All kinds of closed curves, for example C-curves, can be described in this way (see PCT / DK97 / 00223, Figure 1a). One characteristic of these curves is that they will intersect the curve at least once as they are drawn from mathematical poles lying within the section plane. The curves may be symmetrical towards a line in the section plane, and also by a subsequent single Fourier series extension. The piston or chamber will be made easier when the curve of the cross section is symmetrical with reference to a line lying within the section plane through a mathematical pole. This regular curve can be roughly defined by a single Fourier series expansion.

here,

c _p = weighted average value of f (x)

p = expression of triangular alignment.

When a line is drawn from a mathematical polo, it will always cross the curve only once. The specially formed sector of the cross section of the chamber and / or the piston may be approximately defined by the following equation.

here

c _p = weighted average value of f (x)

p = expression of triangular alignment.

Here, in the polar coordinates, this section is expressed by the following approximate expression.

here,

r ₀ ? 0

a≥0

m? 0, m? R,

n? 0, n? R,

0??? 2?

here,

r = Limit of "petal" in the circular cross section of the activation pin

r ₀ = radius of the circular cross section around the axis of the activation pin

a = scale factor for the length of the "frame"

r _max = r ₀ + a

m = parameter for the definition of the "

n = parameter for the definition of the number of "

φ = angle at which the curve is bounded

The inlet is disposed close to the end of the stroke due to the nature of the seal of the piston means.

These particular chambers may be manufactured by injection molding, for example also by use of a so-called super plastic forming method, wherein the aluminum sheet is heated and pressurized by the pressurized air pressure in the tool cavity, .

107a shows a piston 70 having a compression chamber 70 in a longitudinal section having a cylindrical section 71, a transition 72 to a continuous curve 73, and another transition 74 to a substantially cylindrical section 75 Pump. Piston means 76, 76 'are shown at the beginning and end of the pump stroke, respectively. At the end of the outer channel 77, a check valve 78 can be mounted (not shown).

107b shows a piston means 76 comprising an elastic material 79 that provides a generally conical shape in the longitudinal section of the piston at low pressure. The material 79 also functions as a loading means. The bottom part comprises a sealing means 80 which can be folded in the radial direction - this sealing means 80 partly also acts as a loading means. The main support means comprises stiffeners 81 and 82 wherein the stiffener 81 mainly supports the sealing edge 83 of the piston means against the wall of the compression chamber 70 while the other stiffener 82, Transfers the load from the sealing means 80 and the base material 79 to the washer itself supported by the support means 84, for example the piston rod 6. The sealing means 80 is still somewhat folded at this position of the piston means 76 so that higher pressure will be present in the chamber 70 as the folding section 85 causes more loading of the sealing edge 83 . The stiffeners 82 are joined together at the top by joints 86. In this position of the piston means 70 the stiffeners 81 and 82 have an angle between? And? Having a central axis 19, where? Is approximately parallel to the central axis 19 of the compression chamber 70 Do. Angle (? ₁ ) between the surface of the piston (76) and the central axis (19).

Figure 107c shows the piston means 76 'at the end of the pump stroke. The sealing means 80 are folded together while the elastic material 79 is pressed together so that the stiffeners 81 and 82 are oriented substantially parallel to the central axis 19. [ The angle? ₂ between the surface of the piston means 76 'and the central axis 19 is positive, but nearly zero. The distance a 'between the sealing edge 83 and the central axis 19 in the cross section shown is 39% of the distance at the beginning of the stroke. Sealing means 80 '.

Figure 107d shows the transverse section EE of the piston means 76 showing the basic resilient material 79 of the sealing means 80, the stiffeners 81,82 and the folded portion 87. [ Piston rod (6).

107E shows the transverse section FF of the piston means 76 'showing the basic resilient material 79 of the sealing means 80, the stiffeners 81, 82 and the fold 87, . It is clearly shown that the elastic material 79 is squeezed together.

Figure 107f shows a series of transverse cross-sections of the chamber in which the region is reduced to a certain step, while the circumference remains constant - these are defined by two unique modular parametrized Fourier series extensions, one for each coordinate function do. The upper left portion has a cross section which is the starting end face of the series. The set of parameters used is shown at the bottom of the figure. This series shows the decreasing areas of the transverse section. The thicker figures in the figure show the decreasing cross-sectional area of the different shapes with the standard area size at the upper left corner. The cross-sectional area of the shape at the lower right is approximately 28% of the cross-sectional area at the upper left.

107g shows a longitudinal cross-section of the chamber 162, of which the cross-sectional area varies depending on the remaining circumference along the central axis. Piston 163. The chamber has a portion of a different cross-sectional area of its lateral cross-section of the wall sections 155, 156, 157, Transitions (159, 160, 161) between the walls. Sections GG, HH and II are shown. Section GG has a circular cross section, while section HH 152 is approximately 90 to 70% of one of section GG.

Figure 107h shows the cross-section HH 152 and the cross-section GG 150 in Figure 107g as a dotted line. Section HH has an area of approximately 90 to 70% of that of section GG. The transition portion 151 is formed flat. A minimum portion of the chamber having a cross-sectional area of about 50% of the cross-section GG is also shown.

Figure 107i is a transverse section II and a comparison section GG of Figure 107g, shown in phantom. Section II has an area of approximately 70% of that of section GG. The transition portion 153 is formed flat. The minimum portion of the chamber is also shown.

Fig. 107J shows a modified example of the piston of Figs. 107A to 107C in cross section HH from Fig. 107G. The piston is now also made of an elastic material that is impermeable and does not require a separate sealing means. The distances c and d are different and thereby by the deformation of the piston in the same transverse section HH.

107K shows a series of cross-sectional views of the chamber in which the area decreases to a certain level, while the circumference remains constant - they are defined by two unique modular parametrized Fourier series extensions, one for each coordinate function do. The upper left portion has a cross section which is the starting end face of the series. The set of parameters used is shown at the bottom of the figure. Although this series shows decreasing regions of the cross section, it is also possible to increase these regions by keeping the circumference constant. The thicker figures in the figure show the decreasing cross-sectional area of the different shapes with the standard area size at the upper left corner. The size of the cross-sectional area at the lower right is approximately 49% of the size of the starting area at the upper left.

Figure 107L shows a convex curve optimized for a certain fixed length and minimum possible curvature of the boundary curve. The general formula for the minimum radius of curvature corresponding to the maximum curvature of the figure shown in Figure 1071 is as follows.

The length specified by y is determined by the following equation.

here,

r = minimum radius of curvature

L = Boundary - Length = Schedule

A ₁ = Decrease value of starting domain area (A ₀ )

For example, from FIG. 103D, the domain area A ₀ =? (30) ² , and the boundary length L = 60? = 188.5 and corresponds to the area and boundary length of the disk of radius 30. The length is required to be constant, but the area is reduced to the value to be assigned (A ₁ ). The desired final configuration has an area A ₁ = π (19/2) ² = 283.5. The convex curve with the minimum possible curvature of the boundary curve is now,

r = 1.54

虜 = 1 / r = 0.65

χ = 89.4

to be. The curves in the figures are not drawn to scale, only the principles are shown. The curve can also be optimized by replacing the straight line with a curve that can improve the sealing of the piston against the wall.

Figure 107m shows a non-convex curve optimized for a certain fixed length and the minimum possible curvature of the boundary curve. The general formula for the minimum radius of curvature corresponding to the maximum curvature of the figure shown in Figure 1071 is as follows.

The length specified by x is determined by the following equation.

here,

r = minimum radius of curvature

L = Boundary - Length = Schedule

A ₁ = Decrease value of starting domain area (A ₀ )

Non-convex curves (with obvious modifications of the stringed intermediate curves) with the minimum possible curvature of the boundary curves

r = 6.3

虜 = 1 / r = 0.16

χ = 42

to be. The curves in the figures are not drawn to scale, only the principles are shown.

Figures 108a, 108b and 108c illustrate the use of, for example, air (also as an incompressible medium or a combination of compressible and incompressible media, for example as a liquid medium such as water) in a closed chamber constructed as a reinforced hose, For example, as a gaseous medium, as another composite structure comprising a compressible medium. The lining, reinforcement, and cover on the compressed side of the piston means may be possible to be different from those on the uncompressed side, where the skin may be configured as a preformed molded skin to maintain this shape during the pump stroke. It is also possible that the skin is made of two or more parts which are preformed by themselves, one on the uncompressed side of the piston means and the other on the compressed side (cf. part X and part Y + Z in figure 108b). During the pump stroke, the two parts are hinged together (see XY and ZZ in Figure 108B). The adaptation of the sealing edge from the transverse cross-section to the chamber can cause a change in the cross-section of the piston at its sealing edge, which can cause a change in the volume inside the piston. This volume change can provide a change in the pressure of the compressible medium and can cause a changed sealing force. Moreover, the compressible medium functions as a support as it transmits the load on the piston to the piston rod.

Figure 108a shows a longitudinal section of the compression chamber 90 that includes a continuous piston 92 92 at the beginning of the pump stroke and a continuous convex curve 91 with the piston 92 'at its end. The high pressure portion of the chamber 90 includes an outlet channel 93 and an inlet channel 94 having check valves 95 and 96 respectively (not shown). For low pressure purposes, the check valve 95 can be removed.

Figure 108b shows a piston 92 that is directly vulcanized on the piston rod 97 including the compressible medium 103, the reinforcement 100 and the cover 101 in the lining 99. [ The portion X of the skins 99, 100 and 101 is preformed as a portion Y and Z in the compressed portion of the piston means 92. A hinge XY is shown between the portion X and the portion Y of the skin. The portion X has an average angle eta ₁ with the central axis 19 of the compressed chamber 90. The portions Y and Z are connected to each other and have a selected angle of incidence (kappa ₁ ) so that the force can be predominantly directed at the piston rod. The angle [lambda] between the portions (Y ', Z') is chosen such that the greater the force in the chamber, the more perpendicular to the central axis. A hinge (ZZ) between the halves of the part (Z). Sealing edge (102).

Figure 108c shows the piston at the end of the stroke. The portion X 'of the skin now has an angle η ₂ with the central axis while the portion X', Y 'has a side angle (κ ₂ ) and an approximately constant angle between Y' and Z ' (?). The angle between the halves of the portion Z is approximately zero. The distance a 'between the central axis 19 of the chamber and the sealing edge 102 in the illustrated transverse section is approximately 40% of the distance a at the start of the stroke. Sealing edge 102 'and compression medium 103'.

FIGS. 109A, 109B, 109C and 109D show the details of the combination of compression chambers having fixed dimensions and the eighth embodiment of the piston capable of varying its dimensions. The piston is an inflatable body which fills the transverse section of the chamber. During a stroke, it can change its dimension constantly on and near the sealing edge. The material may be a composite of elastically deformable liners and support means such as, for example, fibers (e.g., glass, boron, carbon or aramid), fabrics, filaments, Depending on the fiber architecture and the total final loading on the piston, the piston is shown with a slight internal overpressure, which is roughly a spherical shape or a generally elliptical curve ("rugged" shape) Other shapes can be created. For example, a reduction in the cross sectional area of the chamber results in a reduction in the size of the inflatable body in that direction, and a three-dimensional reduction is possible due to the fiber architecture because the fibers shear independently of each other in the layer direction Based on the 'lattice effect'. The cover is also made of an elastically deformable material suitable for the particular environmental conditions in the chamber. If all of the liner or cover is impermeable, it is possible to use a separate bladder inside the body, since the body comprises gas and / or liquid medium. For example, a supporting means such as a fiber can provide its own strength only if the pressure inside the body is greater than the outside, because they are in tension. This pressure condition may be desirable to obtain a suitable seal and life time. Since the pressure in the chamber may vary constantly, the pressure inside the body should be the same and slightly higher or higher at any point of the pump stroke by keeping it constant at all times. The final solution can only be used for low pressure because the piston can otherwise jam within the chamber. For higher pressures in the chamber, an arrangement may be needed that allows the internal pressure to change accordingly to fluctuations in the pressure in the chamber and also to be slightly higher. This can be accomplished by a number of different arrangement-loading adjustment means based on the principle of changing the volume and / or pressure of the medium inside the piston and / or changing the temperature of the internal medium - for example, An exact selection of the material of the skin of the skin, for example depending on the particular rubber type, other principles are also possible, in which the E-module defining the deformability or the correct selection of the volume of the compressible part of the volume inside the inflatable body And its compressibility. Here, the incompressible medium is used inside the piston. The volume of the piston can be varied by a change in the size of the cross-sectional area at the sealing edge, since the size of the piston in the direction of travel is constant. This change causes the incompressible medium to flow to or from the spring-actuated piston within the hollow piston rod. It is also possible that the spring force operated piston is located at another position. The combination of the pressure caused by the change in the volume of the piston and the change in pressure due to the spring force produces a specific sealing force. The spring force acts as a fine adjustment for the sealing force. Improved load control can be achieved by replacing the incompressible media by a specific combination of compressible and incompressible media, wherein the compressible media operates as a load adjustment means. There is an additional improvement when the spring is replaced by the operating force of the piston of the chamber because it facilitates retraction of the piston due to lower spring force and lower friction. The temperature rise of the medium inside the piston can be achieved particularly when a medium that can be warmed up quickly is selected.

109A shows a longitudinal cross-section of the compression chamber of FIG. 108A with the piston 146 of FIG. 109B at the start of the stroke and the piston 146 'of FIG. 109C at the end of the stroke.

Figure 109b shows a piston 146 having an inflatable body with a wall comprising a fiber 130 having a pattern such that the inflated body is a sphere. Cover 131 and liner 132. Impermeable bladder 133 is shown inside the sphere. The spheres are mounted directly on the piston rod 120. Which is locked at one end by the end cap 121 and at the other end by the cap 122. The hollow channel 125 of the piston rod 120 has a hole 123 in its side in the interior of the sphere so that the loading means in the compressible medium 124 contained within the sphere, 125 to flow freely from / to. The other end of the channel 125 is closed by a movable piston 126 which is loaded by a spring 127. The spring is mounted on the piston rod 128. The spring 127 adjusts the pressure in the sphere and the sealing force. The sealing surface 129 contacts the adjacent walls of the chamber in a substantially line-wise fashion. The fibers are shown only schematically (in all figures of the present application).

Figure 109c shows the piston of Figure 109b at the end of the stroke with the smallest cross-sectional area. The sphere now has a much larger sealing surface 134 that is uniform with the adjacent walls of the chamber. The piston 126 is moved relative to its position as shown in Figure 9B, since the incompressible medium 124 'is squeezed from the distorted sphere. To minimize frictional forces, the cover at the sealing surface may have a rib (not shown) or may have a low friction coating (as well as a chamber wall - not shown). Since none of the caps 121, 122 can move along the piston rod 120, the lattice effect can only be part of the material rest of the skin. The rest is likewise illustrated as a &quot; shoulder &quot; 135 which can significantly reduce life time while increasing friction. Sealing edge 129 '. The distance a 'between the central axis 19 of the chamber and the sealing edge 129' in the illustrated transverse section is approximately 48% of the distance a at the start of the stroke.

109d shows an improved adjustment of the sealing force by having the incompressible medium 136 and the compressible medium 137 inside the sphere. The pressure of the medium is regulated by the piston 138 having the seal ring 139 and the piston rod 140 directly connected to the operating force. The piston 138 can slide within the cylinder 141 of the sphere. The stop portion 145 fixes the ball on the piston rod 140.

Figures 110a, 110b, 110c show an improved piston from which the remainder of the skin can be drained by a small cross-section of the chamber, which means improved life time and less friction. This method relates to the fact that the suspension of the piston on the piston rod can translate and / or rotate on the piston rod to a position remote from the side of the piston where the maximum pressure in the chamber is present. The spring between the movable cap and the stop on the piston rod serves as another loading adjustment means.

Figure 110a shows a longitudinal section of a chamber 169 of a pump according to the invention, each having two positions 168, 168 'of the piston.

110b shows a piston having an inflatable skin with fibers 171 in at least two layers having a fiber architecture that produces a substantially spherical-ellipsoid upon inflation. If the skin is not tightened inside the piston, there may be an impermeable layer 172. The medium is a combination of a compressible medium 173, for example air, and an incompressible medium 174, for example water. The skin 170 is mounted to the end of the piston rod in the cap 175 fastened to the piston rod 176. The other end of the skin is hingedly hinged within the movable cap 177 which can slide on the piston rod 176. The cap 177 is urged toward the compression portion of the chamber 169 by the spring 178 which is pressed at the other end toward the washer 179 fastened to the piston rod 176. Sealing edge (167).

Figure 110c shows the piston of Figure 110b at the end of the pump stroke. The spring 178 'is compressed. The same is valid for the incompressible medium 174 'and the compressible medium 173'. The skin 170 'is deformed and now has a large sealing surface 167'. The distance a 'between the sealing edge 167 and the center axis of the chamber is approximately 43% of the distance a at the start of the stroke.

FIGS. 111A, 111B and 111C show pistons with movable caps for removing the rest of the material at their both ends in the direction of movement on the piston rod. This is an improvement of the piston in the one-way piston pump, but it is now possible to use the piston in a dual-acting pump, specifically with any stroke, and also with the retraction stroke being the pump stroke. Movement of the skin during operation is indirectly limited due to the stop on the piston rod. These stops are positioned so that the pressure of the medium in the chamber can not displace the piston from the piston rod.

FIG. 111A shows a longitudinal section of the chamber with an improved piston 208 at the beginning of the stroke and a piston 208 'at the end.

FIG. 111B shows a ninth embodiment of the piston 208. FIG. The sphere's skin corresponds to that of Fig. The inner impermeable layer 190 is now airtightly compressed within the cap 192 at the bottom into the cap 191 at the top. The details of the caps are not shown, and all kinds of assembly methods can be used. Both caps 191, 192 may translate and / or rotate on the piston rod 195. This can be done in a variety of ways, for example as different types of bearings not shown. The cap 191 at the top can only move upward due to the presence of the stop 196 inside the piston. At the bottom, the cap 192 can only move to the lower layer because the stop 197 prevents upward movement. The &quot; adjustment &quot; of the sealing force includes the combination of the incompressible medium 205 within the sphere and the compressible medium 206, and the spring-actuated piston 126 within the piston rod 195. The medium can freely flow through the holes 207, 200, 201 through the wall 207 of the piston rod. The O-rings (202, 203) in the cap in the cap at the top and at the bottom seal the caps (191, 192) to the piston rod, respectively. A cap 204, shown as a threaded assembly at the end of the piston rod 195, tightens the piston rod. The corresponding stop may be located at another position on the piston rod, depending on the required movement of the skin.

Figure 111c shows the piston of Figure 111b at the end of the pump stroke. The cap 191 is moved over a distance x "from the stop 196 while the bottom cap 192 is pressed against the stop 197. The compressible medium 206 'and the incompressible medium (205 ').

Figures 112 (a), 112 (b) and 112 (c) illustrate improved pistons in connection with the prior art. The improvement should take care of the better adjustment of the sealing force by the smaller sealing contact surface, in particular by the smaller cross-sectional area, by the loading adjustment means. The improved adjustment relates to the fact that the pressure inside the piston is now directly influenced by the pressure in the chamber due to a pair of pistons on the same piston rod, which is independent of the presence of operating force on the piston rod. This can be particularly advantageous in stopping the pump stroke if the operating force is to be changed, for example, because the sealing force is kept constant and no loss of sealing occurs. At the end of the pump stroke when the pressure in the chamber is reduced, retraction will be easier due to the lower frictional force. In the case of a dual working pump, the loading adjusting means can be influenced by both sides of the piston, for example by a dual arrangement of this load adjusting means (not shown). The illustrated arrangement of the pistons conforms to specifications, for example an increase in pressure in the chamber will provide an increase in the pressure of the piston. Other specifications may cause different arrays. The relationship can be designed such that the increment is different from the linear relationship. The configuration is a pair of pistons connected by a piston rod. The piston may have the same area, different size and / or varying area.

Due to the particular fiber architecture and the total final loading - shown with some internal overpressure - the shape of the piston in the longitudinal section is a flattened configuration. In this section, two of the corners act as sealing surfaces, which provide a reduced contact area by means of a smaller cross-section of the chamber. The size of the contact surface can still be increased by the presence of the ribbed outer surface of the piston's skin. The exterior walls of the chamber and / or piston may have a coating, such as, for example, nylon, or may be made of a low friction material.

While sealing one of the three lobed portions and the other (Fig. 7F, e.g., upper and right) at different points of the longitudinal axis of the chamber, while still sealing only one of the three lobed portions at different points, An example having a piston (in this case, by way of example) with three separate pistons according to Figs. 112a to 112c, which seals each other and the boundary curves respectively in one circular cross-sectional area (Fig. 107f, The possibility of a chamber having a transverse cross-sectional shape according to those of Figure 107f is not shown.

FIG. 112A shows a longitudinal cross-section of the piston chamber combination with the tenth embodiment of the piston 222 at the beginning of the stroke in the chamber 216 and the piston 222 'at the end.

FIG. 112B shows a piston whose main configuration is described in FIGS. 11B and 11C. The skin includes ribs 210 on the outside. Inside, the skin and impermeable layer 190 are squeezed at the top between an inner portion 211 and an outer portion 212 which are threaded together. At the bottom, a similar configuration exists in the inner portion 213 and the outer portion 214. Inside the piston, there is a compressible medium 215 and an incompressible medium 219. The pressure in the interior of the piston is adjusted by the piston device which is directly activated by the pressure in the chamber 216. The piston 148 at the bottom connected to the compression chamber 216 is mounted on the piston rod 217 and the other piston 149 is mounted on the other side and connected to the middle part of the piston 222. The piston rod 217 is guided by the slide bearing 218 - other bearing types may also be used (not shown). The pistons on both sides of the piston rod 217 can have different diameters-the cylinder 221 in which the piston moves can even be exchanged by two chambers which may be of the type according to the invention, The pistons also have a type according to the invention. Sealing edge 220. Piston rod 224. The distance d ₁ between the piston 148 and the orifice 223.

112c shows the piston of FIG. 112a at the end of the stroke while there is still a high pressure in the chamber 216. FIG. Sealing edge 220 '. The load adjusting means 148 'has a different distance from the orifice 223 towards the chamber. A piston (148 ', 149') is shown positioned in a distance greater than that (d ₂₎ 112b in Fig from the orifice 223. The

Figs. 113A, 113B and 113C illustrate a combination of a pump of a compression chamber with an elastically deformable wall having different areas of the cross-section and a piston with a fixed geometry. In a housing, for example a cylinder with a fixed geometrical size, an inflatable chamber which is inflatable by a medium (incompressible and / or compressible medium) is located. It is also possible that the housing can be avoided. The inflatable wall includes, for example, a liner-fiber-cover composite portion, or additionally impermeable skin. The angle of the sealing surface of the piston is slightly larger than the comparison angle of the walls of the chamber with respect to the axis parallel to the movement. This difference between the angles and the momentary deformation of the wall by the piston may be slightly delayed (e.g., by precise adjustment of the load adjustment means similar to those shown for viscous incompressible media and / or pistons in the walls of the chamber) ) Provides a sealing edge through which the distance to the center axis of the chamber during the movement between the two pistons and / or chamber pistons can be changed. This provides a change in cross-sectional area during the stroke and thereby a design operable force. However, the cross-section of the piston in the direction of movement also has a negative angle which is equal to or related to the angle of the wall of the chamber-in these cases, the piston's nose must be rounded. In the last-mentioned case, it may be more difficult to provide a varying cross-sectional area and therefore operational force that can be designed. The walls of the chamber may have all of the load control means already shown, such as that shown in Figure 112B, and, if necessary, shape adjusting means. The velocity of the piston in the chamber can affect the seal.

FIG. 113A shows the piston 230 at four positions of the piston in the chamber 231. FIG. Around the inflatable wall is a housing 234 having a fixed geometric size. Within the wall 234 there is a compressible medium 232 and an incompressible medium 233. There may be a valve arrangement for expansion of the wall (not shown). The shape of the piston on the uncompressed side is only an example for showing the principle of the sealing edge. The distance between the end of the stroke and the sealing edge at the start in the illustrated cross-section is approximately 39%. The shape of the longitudinal cross-section may be different from that shown.

Figure 113b shows the piston after the start of the stroke. The distance z ₁ from the sealing edge 235 and the central axis 236. Angle (?) Between the piston sealing edge (235) and the central axis (236) of the chamber. The angle (v) between the wall of the chamber and the central axis 236. The angle v is shown to be less than the angle?. The sealing edge 235 arranges the angle v as large as the angle?. Other embodiments of the piston are not shown.

Figure 113c shows the piston during stroke. The sealing edge 235 and a distance z ₂ from the center axis 236, the distance is smaller than z _1.

Figure 113d shows the piston at the end of the stroke. The sealing edge 235 and a distance z ₃ from the center axis 236, the distance is smaller than z _2.

Figure 114 shows a combination of piston and chamber walls with an interchangeable geometry that allows for continuous sealing, adapting to each other during the pump stroke. The chamber of Figure 13a now only shows the incompressible medium 237 and piston 222 at the beginning of the stroke, while the piston 222 "is shown just before the end of the stroke. The exact choice of the speed of the piston and of the viscosity of the medium 237 can have a positive effect on operation. [0064] The longitudinal cross-sectional shape of the chamber shown in Figure 14 May also be different.

653 Preferred In the embodiment  Explanation for

201a shows a longitudinal section of the piston 5 in the unpressurized state stopped at the first longitudinal position of the chamber 1 in the unpressurized state, and the chamber in the unpressurized state at this position has a circular cross section . The piston 5 may have a manufacturing size approximately the diameter of the chamber 1 at this first longitudinal position. A piston 5 ^* pressurized to a certain pressure level is shown. Any contact length is generated due to the pressure inside the piston 5 ^* .

Figure 201b shows the contact pressure of the piston 5 ^* in Figure 201a. The piston 5 ^* can be jammed in this longitudinal position.

202a shows the piston 5 'at the second longitudinal position of the chamber 1 in the unpressurized state and the longitudinal section of the piston 5 in the unpressurized state stopped at the first longitudinal position, And the second longitudinal position, the chamber has a circular cross section with a constant radius. The piston 5 may have a manufacturing size approximately the diameter of the chamber 1 at this first longitudinal position. The piston (5 ') represents the piston (5) in a non-compressed state located in a smaller cross-section of the second longitudinal position.

Figure 202b shows the contact pressure of the piston 5 'against the wall of the chamber at the second longitudinal position. The piston 5 'can be jammed in this longitudinal position.

202c shows the piston 5 'at the second longitudinal position of the chamber 1 in the unpressurized state and the longitudinal section of the piston 5 in the unpressurized state stopped at the first longitudinal position, And the second longitudinal position, the chamber has a circular cross section with a constant radius. The piston 5 may have a manufacturing size approximately the diameter of the chamber 1 at this first longitudinal position. The piston 5 ' ^{* represents a} piston 5 located at a smaller cross-section of the second longitudinal position and pressurized to the same pressure level as in Fig.

Figure 202d shows the contact pressure of the piston 5 ' ^* against the wall of the chamber at the second longitudinal position. The piston 5 ' ^* may be jammed in this longitudinal position, and the frictional force may be 72 kg.

Figure 203A shows the piston 5 in Figure 201A and the piston 5 " ^* which has been deformed to a pressure level equal to that of the piston 5 ^{* in} Figure 201A. The piston is mainly in the direction of the meridian ), The deformation is induced by the pressure in the chamber 1 ^* .

Figure 203 (b) shows the contact pressure. The piston 5 " ^* can be jammed in this longitudinal position.

FIG. 204A shows a longitudinal section of the piston 15 at a second longitudinal position of the chamber 10 in a non-pressurized state having a circular cross-section. The piston 15 may have a manufacturing size of approximately the diameter of the chamber 10 at this second longitudinal position. The piston 15 ' ^* shows a piston 15 which is pressurized to a certain level and deformed. The deformation is caused because the Young's modulus in the circumferential direction (the cross section of the chamber) is selected to be lower than the Young's modulus in the meridional direction (the longitudinal direction of the chamber).

Figure 204b shows the contact pressure of the piston 15 ' ^* against the wall. This results in an adequate frictional force (4.2 kg) and proper sealing.

204c shows a piston 15 " ^* pressed at a first longitudinal position and a longitudinal section of the piston 15 at a second longitudinal position (manufacturing size) of the chamber 10 in an unpressurized state, the pressure of the piston (15 ^"*) may be identical to the piston (15 ^'*) the pressure (Fig. 4a) at which the position is to the second longitudinal position of the chamber 10. Further, deformation in the circumferential direction and the meridian direction is different.

Figure 204d shows the contact pressure against the wall of the piston 15 " ^* . This results in an appropriate frictional force (0.7 kg) and proper sealing.

Thus, within the diameter range of the selected cross section in this experiment, a piston comprising an elastically deformable container can be sealingly moved in a smaller cross-sectional area and a larger cross-sectional area while maintaining the same internal pressure.

Figure 205 (a) shows a longitudinal section of the piston 15 (manufactured size) and the piston 15 ' ^* at the second longitudinal position of the chamber 10 in an unpressurized state. The piston 15 ' ^* shows the deformed structure of the piston 15 when the piston 15 is pressed. The lower end of the piston 15, 15 ' ^* is attached to the imaginary piston rod to prevent piston movement when chamber pressure is applied.

Figure 205 (b) shows the contact pressure of the piston 15 ' ^* of Figure 205 (a). This pressure is low enough to allow movement of the piston (friction force 4.2 kg) and is suitable for sealing.

Figure 205c shows a longitudinal section of the piston 15 " ^* and the piston 15 (manufactured size), which is pressurized and deformed by the chamber pressure at the second longitudinal position of the chamber 10 ^* in the pressurized state. The lower end of the piston 15, 15 ' ^* is attached to the imaginary piston rod to prevent piston movement when applied. The deformed piston 15 " ^* is approximately twice as large as the undeformed piston 15 Length.

Figure 205d shows the contact pressure of the piston 15 " ^* of Figure 205c. This pressure is low enough to allow movement of the piston (friction force 3.2 kg) and is suitable for sealing.

Thus, when a chamber pressure is applied to a piston comprising a pressurized elastically deformable container, it can be sealingly moved in a longitudinal position having at least the smallest cross sectional area. Stretching due to the force of the applied chamber is large, and it may be necessary to limit this stretching.

Figures 206 to 209 illustrate limiting the stretching of the skin of the piston, which may lead to a contact area that is sufficiently small to permit adequate sealing and sufficient low frictional force to allow movement of the piston. This limits the stretching in the longitudinal direction when the pressure in the chamber is applied or not applied to the vessel and allows lateral expansion when moving from the second longitudinal position to the first longitudinal position of the chamber, And allowing contraction when moving around.

The longitudinal stretching of the container-shaped piston wall can be limited in a number of ways. By reinforcing the walls of the container with fabric and / or fiber reinforcements. It may also be defined by the interior of the chamber of the container located in the expanding body, which is connected to the wall of the container and whose expansion is limited. As another method, for example, pressure management of a chamber positioned between two walls of a container, pressure management of a space above the container, and the like can be used. Further, a stiffener may be disposed outside the piston.

The expansion behavior of the container wall may vary depending on the type of stretching constraint used. Furthermore, the retaining of the piston moving on the piston rod while expanding can be guided by a mechanical stop. The positioning of such a stop may depend on the use of the piston-chamber combination. It may also be the case that the container is guided over the piston rod while being inflated and / or subjected to an external force.

A combination of compressible and incompressible media, compressible media alone, or incompressible media alone, all kinds of fluids can be used.

Since the change in the size of the container is significant from the minimum cross-sectional area with the production size and can expand at the maximum cross-sectional area, for example, communication between the first enclosed space in the piston rod and the chamber in the container may be necessary. In order to maintain the pressure in the chamber, the first enclosed space can also be pressurized at the volume change of the container chamber. At least pressure management for the first enclosed space may be required.

Figure 206a shows an exploded view of an expandable piston 186 including a concave wall 185 and a container 208 'in a second longitudinal position within the chamber 186 and a container 208 at a first longitudinal position within the chamber 186. [ Lt; RTI ID = 0.0 &gt; 186 &lt; / RTI &gt; The center axis 184 of the chamber 186 is shown. The container 208 'represents a size that is approximately the size of manufacture when pressed and has a fabric stiffener 189 within the skin 188 of the wall 187. The wall 187 of the vessel may extend into the staple arrangement 189, which may be a mechanical stop 196 outside the fabric stiffener 189 and / or the vessel 208 Expansion, and / or movement during stroke is stopped by the other stop arrangement. Thus, the container 208 is inflated. Depending on the pressure in the chamber 186, the longitudinal stretching of the vessel wall may still be caused by the pressure in this chamber 186. However, the primary function of the fabric reinforcement is to define this longitudinal stretch of the wall 187 of the vessel 208. As a result, a small contact area 198 is caused. The second main function of the fabric stiffener 189 is to allow contraction when the container moves to the second longitudinal position (and vice versa when expansion is needed). During the stroke, the pressure in the vessels 208, 208 'will remain constant. This pressure is dependent on the change in the volume of the vessel 208, 208 ', thereby changing with the change in the circumferential length of the cross section of the chamber 186 during the stroke. Also, the pressure during the stroke may change. Also, the pressure can vary, depending on or not with the pressure in the chamber 186 during the stroke.

FIG. 206B shows a first embodiment of a piston 208 expanded in a first longitudinal position of the chamber 186. The wall 187 of the container is formed of a skin 188 of flexible material, which may be, for example, a rubber type, and a textile stiffener 189 that allows for expansion and contraction. The direction of the fabric stiffener relative to the central axis 184 (= braid angle) differs from 54 ° 44 '. The change in the size of the piston during the stroke does not necessarily lead to the same shape as shown. Due to the expansion, the thickness of the container wall may be less than the thickness of the container formed when it is positioned in the second longitudinal position of the chamber 186. An impermeable film 190 may be formed inside the wall 187. This impermeable membrane is tightly compressed within the cap 191 at the top of the vessel 208, 208 'and within the cap 192 at the bottom. Although not shown in detail for these caps, all kinds of assembly methods can be used, and these caps can be adjusted themselves according to the thickness variation of the container wall. The caps 191, 192 may both translate and / or rotate above the piston rod 195. Such movements may be implemented in a variety of devices, such as, for example, various types of bearings not shown. The cap 191 at the top of the container can move up and down. A stop 196 on the piston rod 195 outside the vessel 208 defines upward movement of the vessel 208. The lower cap 192 can only move downward because the stop 197 prevents upward movement, and this embodiment can be considered to be used in a piston chamber device with pressure in the chamber 186 below the piston. Other stop arrangements of other pump types, such as dual operation pumps, vacuum pumps, etc., may also be possible, which only vary with design specifications. Other arrangements may be formed to enable and / or define the relative movement of the piston relative to the piston rod. The adjustment of the sealing force may include the combination of the incompressible fluid 205 and the compressible fluid 206 inside the container (which may be used alone), while the chamber 209 of the container may include a spring And can communicate with the second chamber 210 including the piston 126 operated by the force. The fluid (s) can flow freely through the wall 207 of the piston rod and the hole 201. The second chamber can communicate with the third chamber (see FIG. 12), but the pressure inside the vessel can vary with the pressure inside the chamber 186. The vessel may be inflatable through the piston rod 195 and / or by communicating with the chamber 186. The O-rings 202 and 203 and the like in the upper and lower caps seal the caps 191 and 192, respectively, against the piston rod. The cap 204, shown as a screw assembly at the end of the piston rod 195, tightens the piston rod. Depending on the movement required for the vessel wall, a similar stop can be placed elsewhere on the piston rod. There is a contact area 198 between the wall of the vessel and the wall of the chamber.

Figure 206c shows the piston of Figure 206b in a second longitudinal position of the chamber. The upper cap 191 is moved a predetermined distance a 'from the stop 196. The spring force of the valve piston 126 is shifted to a predetermined distance b '. The lower cap 192 is shown adjacent the stop 197 and the chamber 186'can be pressed against the stop 197 when there is pressure in the chamber 186 below the piston. Compressible fluid 206 'and incompressible fluid 205' are shown.

Figure 206d is a three-dimensional view showing the stiffener matrix of the fabric material and enables elastic expansion and contraction of the walls of the vessels 208, 208 'when sealingly moved in the chamber 186. [

The fabric material may be elastic and laid down as separate layers on top of each other. These layers can also be laid together. The angle between the two layers may differ from 54 ° 44 '. If the material type and thickness are the same in all layers and the number of layers is even and the stitch size in each direction is uniform, the expansion and contraction of the wall of the container may be uniform in the X, Y, and Z directions. When the stitches (ss, tt) are inflated, the contraction will become smaller as each becomes larger in the direction of the matrix. Since the material of the seal may be elastic, other devices such as a mechanical stop may be required to stop the expansion. This may be the mechanical stop shown on the piston rod and / or the wall of the chamber as shown in Figure 206B.

Figure 206e is a three-dimensional view showing the expanded stiffener matrix of Figure 206d. The stitches ss 'and tt' are larger than the stitches ss and tt. As a result of the contraction, it can be the matrix shown in Figure 206d.

Figure 206f is a three-dimensional view showing the stiffener of a fabric material made of an inelastic thread (but may be elastically warped), which is laid down on top of each other as an individual layer or interwoven with one another. When the vessel is of manufacture size, and when it is pressurized, it is expandable due to the extra length of each available loop 700 when placed in the second longitudinal position of the chamber. The stitches ss' ', tt "' lie in each direction. When the wall of the container expands, the inelastic material (but may be elastically warped) may limit the maximum expansion of the wall 187 of the container 217. It is necessary to stop the movement of the container 217 on the piston rod 195 by, for example, the stop 196 so that the seal can be maintained. The lack of such stop 196 can provide valve buildability.

Figure 206g is a three-dimensional view showing the inflated matrix of the inflated figure 206f. The stitches ss' '' and tt '' 'are larger than the stitches ss'' and tt '' '. As a result of the contraction, it can be the matrix shown in Figure 206F.

Figure 206h shows three steps (I, II, III) of the manufacturing process of the piston including the elastically deformable container. A rubber manchet 401 is disposed on the rod 400 and a reinforcing mandchet 402 according to, for example, Figs. 406E to 406G is disposed thereon. On top of that there is another rubber manmade cave. One or more caps 404 may be disposed between the manganese cobalt 401 and the rod. All of which can slide on the rod 400. The rod 400 may be hollow and may be connected to a high pressure steam source. Step II: Pressurized vapor may be introduced into the cave 408 of the oven 406 by way of the outlet 405, which may be placed at the end of the rod. The complete rubber / stiffener mandchet 407 side can be cut and can be transferred into the cave 408 on the rod 400. The cave can then be closed, and the pressurized steam is injected into the cave. A vulcanization process may be performed, including mounting the walls of the container on the cap 404. Manchat can take the form of a curve. After the vulcanization process, the cave can be opened and the container with the production size is withdrawn (step III). Various methods can also be used to produce other pistons using the vulcanization time of the piston. Bulging of the rubber manganite cakes 407 (including the fabric reinforcements) can be accomplished prior to the vulcanization process. The rod 400 may be divided into a number of parts, each approximately similar to the height of the container of manufacture size. Each component can be detached from the main rod before entering the cave. And / or a plurality of caves may be present at the end of the manufacturing feed line, each of which lines uprightly receives a full manganese chelate 407 and vulcanizes. This can be done by a translating and / or rotating cave from the end of the manufacturing supply line and to its end. A plurality of vulcanized caves can be integrated into the manufacturing supply line.

Figure 207a is a cross-sectional view of a chamber 186 having a concave wall 185 and a chamber 187 having an expandable piston including a container 217 in a first longitudinal position of the chamber and a container 217 ' Fig. The container 217 'is pressurized to indicate the approximate manufacturing size.

Figure 207b shows the piston 217 expanded at the first longitudinal position of the chamber. The wall 218 of the vessel may be formed by a skin 216 of elastic material which may be, for example, a rubber type, and a fiber reinforcement 219 according to the lattice effect (Grid Effect) allowing the expansion of the vessel wall 218 . The direction of the fibers (= braid angle) with respect to the central axis 184 may be different from 54 ° 44 '. There is a contact area 211 between the wall 218 of the container 217 and the wall 185 of the chamber 186. The thickness of the container wall due to expansion may be smaller, but does not necessarily have to be very different from the thickness of the container formed when placed in the second longitudinal position. The impermeable film 190 may be present inside the wall 187. This impermeable membrane is tightly compressed within the cap 191 at the top of the container 217, 217 'and within the cap 192 at the bottom. Although not shown in detail for these caps, all kinds of assembly methods can be used, and these caps can be adjusted themselves according to the thickness variation of the container wall. The caps 191, 192 may both translate and / or rotate above the piston rod 195. Such movements may be implemented in a variety of devices, such as, for example, various types of bearings not shown. The cap 191 at the top of the vessel can move up and down until the stop 214 defines movement. The lower cap 192 can only move downward because the stop 197 prevents upward movement, and this embodiment can be considered to be used in a piston chamber device with pressure in the chamber 186 below the piston. Other stop arrangements of other pump types, such as dual operation pumps, vacuum pumps, etc., may also be possible, which only vary with design specifications. Other arrangements may be formed to enable and / or define the relative movement of the piston relative to the piston rod.

During the stroke, the internal pressures of the vessels 217 and 217 'can be kept constant. Also, the pressure during the stroke may change. The adjustment of the sealing force may include a combination of the incompressible fluid 205 and the compressible fluid 206 inside the vessel (which may be used alone), while the chamber 215 of the vessels 217 and 217 ' (210) including a piston (126) actuated by a spring force within the first chamber (195). The fluid (s) can flow freely through the wall 207 of the piston rod and the hole 201. The second chamber can communicate with the third chamber (see FIG. 210), but the pressure inside the vessel can vary with the pressure inside the chamber 186. The vessel may be inflatable through the piston rod 195 and / or by communicating with the chamber 186. The O-rings 202 and 203 and the like in the upper and lower caps seal the caps 191 and 192, respectively, against the piston rod. The cap 204, shown as a screw assembly at the end of the piston rod 195, tightens the piston rod.

Figure 207c shows the piston of Figure 207b in a second longitudinal position of the chamber 186. The contact area 211 'is small. The cap 191 is moved from the stop 216 to a predetermined distance c '. The spring-actuated valve piston 126 has been moved a predetermined distance d '. The lower cap 192 is shown adjacent to the stop 197 and when there is pressure in the chamber 186 the cap 192 is pressed against the stop 197. The compressible fluid 206 'and incompressible fluid 205', whose volume can be varied in the vessel, are shown.

Figures 208a, 208b and 208c are similar to Figure 207a except that the reinforcement comprises any type of reinforcement means that can be laid and bent in a pattern of stiffeners &quot; colums &quot; 207B, and 207C of the second embodiment of the present invention. This pattern may be a pattern parallel to the central axis 184 of the chamber 186 or a pattern in which a portion of the stiffening means may be in a plane passing through the central axis 184. [

FIG. 208A illustrates a container 228 at a first longitudinal position of the chamber 186 and an expansion 228 'at a second longitudinal position of the pressurized chamber 186 with a non- Fig.

208B shows the container 228 at a first longitudinal position of the chamber 186. The container 188 is shown in Fig. The wall 221 of the container includes elastic materials 222 and 224 and a reinforcing means 223 such as a fiber. Impermeable film 226 may be present. There is a contact area between the vessel 228 and the wall 185 of the chamber 186.

FIG. 208C shows the container 228 'in the second longitudinal position of the chamber 186. FIG. The contact area 225 'may be slightly larger than the contact area 225. The upper cap 191 has moved from stop 214 by e '.

Figure 208d shows a top view of pistons 228 and 228 'with reinforcing means 223 and 223 &quot;, respectively, at a first longitudinal position and at a second longitudinal position of chamber 186.

Figure 208E shows a top view of the piston, such as pistons 228 and 228 ', with an alternative embodiment of the stiffening means 229 and 229', respectively, at a first longitudinal position and a second longitudinal position of the chamber 186 . A portion of the stiffener does not lie in a plane that passes through the central axis 184 in the longitudinal direction of the chamber 186. Figure 208f shows a top view of the piston, such as pistons 228 and 228 ', with stiffeners 227 and 227' on the walls of the vessel in a plane that does not pass through the central axis 184 of the chamber 186. During the stroke, the walls of the container rotate about the central axis 184.

208g schematically illustrates how the fibers 402 can be mounted to the cave 431 of the cap 430. Fig. This can be done by rotating the cap and fiber around the central axis 803 and when the fibers 432 are being pushed towards the cave 431, the cap and the fiber can each have their own speed.

Figure 209a shows a longitudinal section view of a chamber 186 with an expandable piston that includes a convex wall 185 and a container 258 at the start of the stroke and a container 258 'at the end of the stroke. The container 258 'is pressed in the second longitudinal position.

209b includes a skin reinforced by a plurality of at least elastically deformable support members 254 rotatably secured to a common member 255 and connected to the skins 252 of the pistons 258 and 258 ' A longitudinal section view of one piston 258 is shown. The members are subjected to tension and have some maximum stretching length depending on the hardness of the material. This limited length defines the stretching of the skin 252 of the piston. The common member 255 may slide with the sliding means 256 on the piston rod 195. The remaining structure is the same as that of the piston 208, 208 '. The contact area 253 is shown.

Figure 209c shows a longitudinal section of the piston 258 '. The contact area 253 'is shown.

210 to 212 deal with pressure management inside the container. Managing the pressure of the piston, including the inflatable container with the elastically deformable wall, is an important part of the piston-chamber structure. To maintain the seal at the proper level, the pressure must be maintained to maintain the pressure in the container. This means that the volume of the vessel changes during each stroke. And, in the long term, the pressure in the container may be reduced due to leakage from the container, which may affect the sealing ability. Fluid flow can be a solution. The flow of fluid from the container to the container and / or to a container such as the (inflator) described above can be resolved when the volume during the stroke changes.

The change in the volume of the container will balance, for example, the volume change of the first enclosed space communicating with the container through the hole in the piston rod. At the same time, the pressure can be balanced and this pressure balance can be achieved by a spring-actuated piston which can be placed in the first closed space. A spring force can be generated by a spring or a pressurized airtight space, for example, a second airtight space communicating with the first airtight space by a pair of pistons. Any kind of force transmission can be arranged by each piston, for example, by a combination of the second enclosed space and the piston in this case, so that when the piston pair moves toward the first enclosed space, The force on the piston in the first closed space remains the same but the force on the piston in the second closed space is reduced. This is consistent with the rule that p.V = constant in the second enclosure. Further, the pressure adjustment in the container chamber at all or a part of the stroke can be achieved by the communication of the chamber and the container chamber. This is already disclosed in International Patent Publication No. WO 00/65235 and International Publication No. WO 00/70227.

The container may be inflated through a handle in the piston rod and / or the piston rod. The valve may be a check valve or an expansion valve, for example a shrouder valve. The container may be inflated through a valve in communication with the chamber. If an expansion valve is used, a shrouder valve having the ability to prevent leakage and the ability to control all kinds of fluids is desirable. To enable expansion, for example, a valve actuator disclosed in International Publication No. WO 99/26002 or U.S. Patent No. 5,094,263 may be required. The valve actuator of International Publication No. WO 99/26002 is very practical when manually inflated because it can be inflated with very little force. Also, in combination with a valve having a spring-actuated valve core, the valve automatically closes when the same pressure level is obtained.

If the flow of the pressurized volume from the enclosed space to the container and vice versa can be significant, then a pressure / volume source having a pressure level equal to, lower than, or higher than the pressure in the container and having a volume greater than the volume of the enclosed space May be preferred. The volume of the pressure source may be reduced relative to the pressure source having a pressure level equal to the pressure level of the vessel, if the pressure source has a pressure level equal to, lower than, or higher than the pressure in the vessel.

If the pressure level in the pressure source is higher than the pressure level of the vessel, during the stroke, the flow between the pressure / volume source and the vessel needs to be steered by the valve. These valves may have a spring force-actuated core pin that can be driven. The actuator can open / close a valve that continuously changes the flow uniformly. A similar structure used to inflate a container due to a pressure drop due to leakage (see next page) is illustrated. Other valve types and valve adjustment solutions are possible. This may be a method of continuously maintaining the pressure level in the vessel at a predetermined level.

By communicating the valve with the chamber, the container can be &quot; automatically &quot; inflated when the pressure in the container is lower than the pressure in the chamber. Even if this is not the case, a higher pressure may be temporarily created in the chamber by closing the outlet valve of the chamber near the second longitudinal position of the chamber in the chamber. Such opening and closing can be performed manually, for example, by a valve actuator (International Publication No. WO 99/26002) and, for example, by a pedal opening a channel communicating with a space between the shrouder valve. On opening, the valve actuator can move, but the valve actuator does not have enough force to press against the core pin which is actuated by the spring force of the valve, so that the shrouder valve is not opened, so that the chamber can be closed, Some large pressure may be formed. When the channel is closed, the actuator functions as disclosed in WO 99/26002. The operator can check the pressure in the container through a pressure gauge, for example, a pressure gauge. In addition, opening and closing of the outlet valve can be performed automatically. This can be done by any kind of means that initiates the closing of the outlet with any kind of signal, by measuring the pressure below a predetermined value.

By means of a combination of the chamber and a valve, for example a valve in communication with the release valve of the container, the container can automatically expand to any desired value. At a predetermined pressure, for example, in a space or chamber above the container. Alternatively, when the predetermined pressure is reached, the valve actuator of International Publication No. WO 99/26002 can be opened first, for example, in combination with a spring. Alternatively, when the pressure reaches a predetermined value or more, the opening to the valve actuator can be closed by, for example, a spring-actuated piston or cap. Alternatively, when any pressure is reached (not shown), the piston can be closed by combining the piston 292 of Figure 211e with the means of causing the channel 297 to open.

210A shows a piston-chamber system with a piston including a vessel 208, 208 'and a chamber 186 with a central axis 184 according to FIGS. 206A-C. The expansion and pressure management described herein can be used for other pistons, including the vessel. Vessels 208 and 208 'may be inflated through valve 241 in handle 240 and / or valve 242 in piston rod 195. If the handle is not used, for example, the rotation axis may be a hollow shape communicating with a shroud valve or the like. The valve 241 may be an expansion valve, such as a shrouder valve, including a bushing 244 and a valve core 245. The valve in the piston rod 195 may be a check valve having a flexible piston 126. The chamber between the check valve 242 and the chamber 209 of the vessel 208, 208 'was initially described as a' second chamber '210. The pressure gauge 250 is capable of controlling the pressure inside the container and is not shown in more detail. It is also possible to use this pressure gauge to control the pressure in the chamber 186. In addition, the chamber 209 of the vessels 208, 208 'has a release valve (not shown) that can be adjusted to any desired pressure. The ejected fluid may be directed to the chamber 209 and / or the space 251.

Fig. 210B shows an alternative of the expansion valve 241. Fig. Instead of the expansion valve 241 in the handle 240, there may be only a bushing 244 without a valve core 245, which may be connected to a pressure source.

210c shows the bearing 246 of the rod 247 of the check valve 126 in detail. The bearing 246 includes a longitudinal duct 249 that allows fluid to pass around the rod 247. The spring 248 may apply pressure to the fluid in the second chamber 210. A stop 249 is shown.

210d shows the flexible piston 126 of the check valve 242 in detail. The spring 248 maintains the pressure against the piston 126.

Figure 210E shows a pressure source 451 that may have a pressure that exceeds the pressure level of the vessel. For example, an inlet valve 452 with a valve actuator 453 (the structure 459 shown is similar to the structures 292 and 297 of Figure 211E) and an outlet valve 454 with a valve actuator 455 ) (The structure 451 shown is similar to the structures 292 and 297 in Figure 211E). The space 460 is connected to the chamber 457 while the space 462 is connected to the chamber 458. Valves 452 and 454 may be mounted to a piston rod 456 which may be split into two chambers 457 and 458.

FIG. 210f shows the structure of FIG. 210e, showing two black boxes each including a valve arrangement adjustable by an external signal. Steering 415 may receive pressure signals 416 and 417 from the interior of the piston at different longitudinal positions of the chamber, respectively. The steering 415 may transmit signals 418 and 419 to the actuator 422 of the outlet valve arrangement 420 and the actuator 423 of the inlet valve arrangement 421, respectively. This valve and valve steering arrangement may be similar to that shown in Figure 211f.

Figure 211a illustrates a piston-and-piston assembly with a piston having a central portion including the same vessels 248 and 248 'as the vessels 208 and 208' and a chamber 186 with a central axis 184 according to Figures 206a through 206c. Chamber system. The expansion and pressure management described herein can be used for other pistons, including the vessel. The vessel 208, 208 'may be inflated through a valve in communication with the chamber 186. This valve may be a check valve 242 according to FIGS. 210A and 210D, or it may be an expansion valve, preferably a shrouder valve 260. The first enclosed space 210 communicates with the chamber 209 in the container by the hole 201 while the first enclosed space 210 communicates with the second enclosed space 243 through the piston arrangement, 2 enclosure may be expanded through an expansion valve or the like, such as a shrouder valve 241, which may be disposed within the handle 240. The valve has a core pin 245. If the handle is not used, for example, the axis of rotation may be hollow and the shrouder valve may communicate with this channel (not shown). The shrouder valve 260 has a valve actuator 261 according to International Publication No. WO 99/26002. The receiving portion 262 of the chamber 186 may have an outlet valve 263, e.g., a Schrader valve, to which another valve actuator 261 according to WO 99/26002 may be mounted. The pedestal 262 can be mounted with a pedal 265 rotatable about an axis 264 on the pedestal 262 by an angle a in order to manually control the outlet valve 263. The pedal 265 is connected to the piston rod 267 by an axis 266 in the non-circular hole 275 above the pedal 265. The pedestal 262 has an inlet valve 269 (not shown) for the chamber 186. A spring 276 (shown schematically) holds the pedal 265 in an initial position 277 where the outlet valve is held open. At the operating position 277 'of the pedal 265, the outlet valve is closed and held. An exit channel 268 is shown.

FIG. 211B shows in detail the communication between the first closed space 210 and the second closed space 243 by the pair of pistons 242 and 270. FIG. The piston rod 271 of the pair of pistons is guided by the bearing 246. The longitudinal duct 249 in the bearing 246 can transfer fluid from the space between the bearing 246 and the pistons 242, A spring 248 may be present. A piston rod 195 of a piston type vessel 248, 248 'with an inner wall 194 is shown. The pistons 242, 270 are sealed against the inner wall 194.

Figure 211c shows another wall 273 of the piston rod 272 of the piston type vessel 248, 248 'having an angle [beta] with respect to the central axis 184 of the chamber 186. A piston 274 is shown schematically, and the piston itself may be configured to accommodate a change in cross-sectional area within the piston rod 272.

Figure 211d shows the piston 248 'on which the housing 280 is formed. The housing includes a shrouder valve 260 and a core pin 245. Fluid may be introduced into valve 260 through channels 286, 287, 288, 289 although valve actuator 261 is shown pressing core pin 261. When the core pin 245 is not pressed, the piston ring 279 will seal the wall 285 of the inner cylinder 283. The inner cylinder 283 can be sealed closed by the seal 281, 284 between the housing 280 and the cylinder 282. A chamber 186 is shown.

FIG. 211E shows the structure of the outlet valve 263 with the core pin 245 shown as being pressurized by the valve actuator 261. FIG. Fluid can flow through the channels 304, 305, 306, 307 to the open valve. The inner cylinder 302 is sealed closed between the housing 301 and the cylinder 303 by the sealing portions 281 and 284. [ A channel 297 with a central axis 296 is disposed through the walls of the inner cylinder 302, the cylinder 303, and the wall of the housing 301. An opening 308 of the channel 297 is provided outside the housing 301 and the expansion portion 309 of the opening allows the piston 292 to be sealed by the upper portion 294 in the closed position 292 ' . The piston 292 may move within another channel 295 that may have the same center axis 296 as the channel 297. [ A bearing 293 for the piston rod 267 of the piston 292 is shown. The piston rod 267 may be connected to a pedal 266 (see FIG. 211A) or another actuator (shown schematically in FIG. 211E).

FIG. 211Ea shows the state after FIG. 218B.

Figure 211f shows the piston 248 'and expansion arrangement 368 of Figure 211d as well as the arrangement 369 for adjusting the outlet valve of Figure 211e. The expansion arrangement 368 now also includes an arrangement 370 for controlling the valve of Figure 211E. The arrangement 370 can operate to open the valve when the valve is closed when the predetermined pressure is reached and when the pressure is lower than a predetermined value. Signal 360 is processed in transducer 361 which transmits signal 362 to actuator 363 which actuates piston 292 through actuation means 364. [

The arrangement 369 for regulating the opening and closing of the outlet valve 263 when the chamber has an operating pressure which is lower than the predetermined pressure in the piston is controlled by means 365 initiated by the signal 365 from the transducer 361 367 via the other actuators 363. The measuring instrument in the chamber that transmits the signal 371 to the transducers 361 and / or 366 can automatically detect whether the actual pressure of the chamber is lower than the operating pressure of the piston. This can be done particularly when the pressure of the piston is lower than the predetermined pressure.

Figure 211g schematically illustrates a cap 312, 312 'with a spring 310 connected to the housing 311 of the valve actuator 315. The spring 310 can maintain the aperture 314 in a tightly closed condition. The contact area 313 of the cylinder 282 (Figure 211d) and the cap 312 is shown. When the force exerted from the chamber to the cap 312 is greater, the cap can move to the position where the cap 312 'is shown until it equilibrates with the forces exerted on the cap by the media / media of the chamber. The spring 310 may determine the maximum pressure value that presses the valve core pin 245. Shrouder valve 260 is shown.

Figure 212 shows a three-piece piston rod 320 positioned at the end of a piston rod 323 from which a pair of pistons 321, 322 can move within the bearing 324.

Figures 213a, 213b and 213c illustrate a combination of a pump, a pressure chamber with an elastically deformable wall of differing cross sectional area, and a piston with a constant geometric shape. For example, an inflatable chamber is disposed in a housing as a cylinder with a constant geometric size, which can be inflated by fluid (incompressible and / or compressible fluid). Also, the housing may be absent. The inflatable wall may include, for example, a liner-fiber-cover composite, or an impermeable skin may be added. The angle of the sealing surface of the piston is slightly larger than the comparison angle of the chamber wall in relation to the axis parallel to the movement. This angular difference and the instantaneous deformation of the wall by the piston are implemented with a slight delay (e.g., by having a viscous incompressible fluid in the walls of the chamber and / or by correcting the load adjustment means, which may be similar to that shown for the piston Due to the fact that the seal edge is provided and the distance of the sealing edge to the center axis of the chamber during movement between the two pistons and / or chamber positions may vary. This changes the sectional area during the stroke, thereby providing a desired operating force. However, the cross section of the piston in the moving direction is constant or has a negative angle with respect to the angle of the chamber wall, and in this case, the 'nose' of the piston is rounded. In this case, it becomes more difficult to change the cross-sectional area, and it becomes difficult to provide a desired operating force. All of the load adjusting means already shown can be mounted on the wall of the chamber (one is shown in Figure 212B), and if necessary, shape adjusting means can also be mounted. The piston speed in the chamber can affect the seal.

FIG. 213A shows the piston 230 at four positions in the chamber 231. FIG. Around the inflatable wall, the housing 234 has a constant geometric dimension. Within the wall 234 there is a compressible fluid 232 and an incompressible fluid 233. There may be a valve arrangement for inflating a wall (not shown). The shape of the piston on the non-pressure side is only an example for illustrating the structure of the sealing edge. The distance between the sealing edge at the end of the stroke and the sealing edge at the start of the stroke in the illustrated cross-section is approximately 39%. The shape of the longitudinal cross-section may be different from the illustrated shape.

Figure 213 (b) shows the piston after the stroke has started. Z ₁ is the distance between the sealing edge 235 and the central axis 236. The angle between the piston sealing edge 235 and the center axis 263 of the chamber is?. The angle between the chamber wall and the central axis 236 is v. The angle? Is shown to be smaller than the angle?. The sealing edge 235 is arranged such that the angle? Is increased by the angle?. Other embodiments of the piston are not shown.

Figure 213 (c) shows the piston during the stroke. The distance between the sealing edge 235 and the central axis 236, and Z _2, is smaller than the distance Z _1.

Figure 213 (d) shows the piston at the end of the stroke. The distance between the sealing edge 235 and the central axis 236, and Z _3, Z ₂ is less than this distance.

Figure 214 shows a combination of a wall of the chamber and a piston with a 2-28 geometry that is adaptable to each other during the pump stroke while being capable of continuous sealing. Which has a fabrication size at the second longitudinal position of the chamber.

Now, although FIG. 213A shows a chamber with only incompressible medium 237 and piston 385 at the start of stroke, the piston 385 'just before the stroke is shown. In addition, any other embodiment of a piston whose dimensions may vary may also be used herein. By accurately selecting the velocity of the piston and the viscosity of the medium 237, it can have a positive effect on operation. The longitudinal cross-sectional shape of the chamber shown in Fig. 14 may also be different.

215A-215F illustrate an embodiment of a chamber of different cross-sectional size with a constant circumferential size. This is another solution for the problem of the jam of the piston cited in WO 00/70227. When reinforcement of the skin allows a portion of the wall of the vessel having a different distance from the central axis of the chamber to be used in the longitudinal cross section of the chamber, for example, at the position of the reinforcement of Figure 208d substantially parallel to the central axis of the chamber, And when, for example, an elastic seal (Figs. 206d, Fig. 206e) or an elastic seal shown in Figs. 206f and 206g allowing individual sizes is made, the piston according to claim 1 functions well in these particular chambers . The pistons shown in Figures 209a and 209b may also function well. A piston having an inelastically deformable container or an elastically deformable container of a manufacturing size approximately equal to the size of the circumferential length of the first longitudinal position of the chamber and having a stiffener allowing contraction with high frictional force, And can also be jammed in chambers having different circumferential sizes in cross-section. If the braid angle of the container stiffener can be 54 ° 44 ', the otherwise elastically deformable container becomes inelastically deformable, that is, it is flexible and deformable, but not jammed within these chambers . If the variation of the cross sectional area of the piston and / or the chamber between two positions in the direction of motion is continuous but large enough to cause leakage, it is desirable to minimize changes in other parameters of the cross section. This can be explained using a circular cross section (fixed shape): the circumference of the circle is πD and the area of the circle is 1 / 4πD ² (D = circle diameter). That is, the reduction of D leads to a linear reduction of the circumference and a 1/4 reduction of the area. It is possible to reduce the area while maintaining the circumference. Further, even when the shape is fixed, for example, in a circle, there is a minimum area. If the shape is a variable, advanced numerical computation can be performed using the Fourier series expansion described below. The cross-section of the pressure chamber and / or the piston may have any shape, which may be defined by one or more curves. The curves are closed curves and can be roughly defined by two unique modular parametrized Fourier series expansions, one for each coordinate system function,

here,

A cosine weighted average value of C _p = f (x)

the sign weighted average value of d _p = f (x)

p = degree of trigonometric function.

Figures 215A and 215E illustrate examples of such curves using a series of different variables in the following formulas. In these examples, only two variables were used. If more coefficients are used, another important requirement is found, for example, that the curve has an optimized curve that meets the maximum tensile in the portion of the curve with the specified maximum radius and / or in the sealing portion that does not exceed a certain maximum under a given premise can do. For example, FIG. 215F shows optimized convex and non-convex curves used for possible transformation of the domain coupled in the plane under the constraint that the length of the boundary curve is fixed and its numerical curvature is minimized have. Using the starting area and starting boundary-length, a minimum possible curvature for a specific desired target area can be calculated.

The piston shown in the longitudinal section of the chamber is mainly shown for the case where the boundary curve of the cross section is circular. That is, for example, in the case where the chamber has a transverse section according to the non-circular cross-section of Figs. 215A, 215E and 215F, the shape of the longitudinal section of the piston may be different.

All kinds of closed curves can be described by this formula, for example, the C-curve (PCT / DK97 / 00223, see FIG. 1A). One characteristic of these curves is that when you draw a line from a mathematical pole placed in the section plane, it intersects the curve at least once. The curves are symmetrical towards the line of the section plane and can be generated along a single Fourier series expansion. The piston or chamber will be easier to manufacture if the curve of the cross section is symmetrical about the line lying in the section plane passing through the mathematical pole. This normal-curve can be roughly defined as a single Fourier series expansion.

here,

C _p = weighted average value of f (x)

p = degree of trigonometric function.

Drawing a line from a mathematical pole, this line crosses the curve only once.

The cross-sectional sector of the particular type of chamber and / or piston can be roughly defined by the following formula:

here,

C _p = weighted average value of f (x)

p = degree of trigonometric function.

And, in polar coordinates, this section is expressed by the following formula.

here,

Here,

r = limit of "petal" in the circular cross-section of the actuating pin,

r ₀ = radius of the circular section around the axis of the actuating pin,

a = conversion factor for "petal" length,

r _max = r ₀ + a,

m = variable to define the "Petal" width,

n = variable for defining the number of "petals"

Ψ = angle defining the curve.

The inlet is disposed close to the end of the stroke due to the nature of the sealing area of the piston means.

These particular chambers may be manufactured by injection molding and may be manufactured using a so-called superelastic forming method, for example, heating the aluminum sheet to form using the motion of the tool or squeezing it into a forced air pressure within the tool cavity.

Figure 215a shows a series of transverse cross-sections of a constant chamber while the area is reduced in certain steps, which are defined by two unique modular parametrized Fourier series expansions, one for each coordinate system function. And the upper left side is a cross section that is the starting end face in the above series of cross-sections. The set of variables used is shown at the bottom of the figure. This series of cross-sections shows the area reduction of the cross-section. The figures in bold in the figures show the cross-sectional area decreasing to a different shape, and the numerical value at the upper left corner is the starting area size.

The cross-sectional area of the shape at the lower right is approximately 28% of the cross-sectional area at the upper left.

215B shows a longitudinal cross section of the chamber 162, wherein the cross sectional area of the chamber is varied by maintaining the circumference along the central axis. A piston 163 is shown. The chamber has a portion of different cross-sectional area of the cross-section of the wall sections 155, 156, 157, 158. There are transitions 159, 160 and 161 between the wall sections. Sectional views (G-G, H-H, I-I) are shown. The cross-section (G-G) has a circular cross-section while the cross-section (H-H 152) has an area of 90 to 70% of the cross-sectional (G-G) area.

Figure 215c shows the lateral cross section (H-H 152) of Figure 207g, and the cross section (G-G 150) is shown as a dashed line for comparison. The section (H-H) has an area of 90 to 70% of the approximate section (G-G) area. A smoothly formed transition 151 is shown. A minimum portion of the chamber is also shown, which has an area of about 50% of the cross-sectional area of the cross-section (G-G).

FIG. 215D shows the cross-section (I-I) of FIG. 207G, and the cross-section (G-G 150) is shown by broken lines for comparison. The section (I-I) has an area of 70% of the approximate section (G-G) area. The transition portion 153 is smoothly formed. A minimum portion of the chamber is also shown.

Figure 215e shows a series of transverse cross-sections of a constant chamber while the area is reduced in certain steps, which are defined by two unique modular parameterized Fourier series expansions, one for each coordinate system function. And the upper left side is a cross section that is the starting end face in the above series of cross-sections. The set of variables used is shown at the bottom of the figure. This series of cross-sections shows the area reduction of the cross-section, but it is also possible to increase these areas by keeping the circumference constant. The figures in bold in the figures show the cross-sectional area decreasing to a different shape, and the numerical value at the upper left corner is the starting area size. The cross-sectional size of the lower right is approximately 49% of the size of the starting area at the upper left.

Figure 215f shows a convex curve optimized for some fixed length of the boundary curve and the minimum possible curvature. The general formula for the minimum radius of curvature corresponding to the maximum curvature of the figure shown in Figure 71 is:

The length specified by y is determined as follows:

here,

r = minimum radius of curvature

L = Boundary - Length = Schedule

A ₁ = reduced value of starting domain area (A ₀ )

As illustrated in FIG. 203D: the domain area A ₀ =? (30) ² and the boundary length L = 60? = 188.5 correspond to the area and boundary length of the disk with a radius of 30. The length should be constant, but the area decreases to a specified A ₁ value. The desired final structure should have the area A ₁ = π (19/2) ² = 283.5. The convex curve with the minimum possible curvature of the boundary curve is:

r = 1.54

k = 1 / r = 0.65

x = 89.4

The curves in the figures are not drawn to scale, and the figures only show the principle.

By replacing the straight line with a curve that can improve the sealing of the piston against the wall, the curve can be further optimized.

Figure 216 illustrates an elastically deformable container 372 that is centered about a central axis 370 that moves within a chamber 375 within a cylinder wall 374 and a tapered wall 373, As shown in Fig. The piston is actuated in at least one piston rod 371. Containers 372 and 372 'are shown in a second longitudinal position and a first longitudinal position 372 of the chamber 372'.

All of the solutions described herein can be combined with a piston type in which a chamber with a constant circumferential size cross-section can be a solution for the problem of jamming.

Figure 217a shows the convex chamber 380 inside the wall 381. "s" means administration.

Figure 217b shows a force-stroke graph in the direction shown in Figure 217a. This curve shows an optimized variation of the force when the operator pumped in a stroke where the fluid inlet is approximately located at the first longitudinal position of the chamber and the outlet is approximately at the second longitudinal position of the chamber. The curve approximates the maximum operating force at the end of the pumping stroke.

218a shows an example of a moveable power unit 390 shown moveably by a parachute 391 and a wheel 392. Fig.

Figure 218b shows a movable power unit 390, which includes a set of solar cells 393 and a motor 394 on top. A water pump 395 and a compressor 396 are also shown. A steering unit 397 is shown.

FIG. 211E 'shows a modification to the outlet valve shown in FIG. 211E. The piston rod 267 is connected to the second channel pin 8001. The channel pin is installed in the guide channel 8002. The channel pin seals the equalization channel 8003. The channel pin has a hole and when the piston rod 267 pushes the piston 292 against the opening 308 of the channel 297 the hole permits flow through the channel 8003. The equalization channel connects the channels 305, 306, 307 in the valve with the outflow chamber 8004. The outlet chamber may be an outlet chamber of the valve. This arrangement is used when the pressure formed in the inlet chamber of the valve is insufficient to actuate the valve and a low pressure from the outlet chamber of the valve may be used to trigger the operation of the valve.

507 Description of the Preferred Embodiment

Figure 301 shows a valve actuator in a clip-on valve connector, for example, coupled to a shrouder valve. The piston 477 is disposed in close proximity to the first end 492 of the cylinder 470. The connector has a housing (500) and the sealing means includes one annular portion (475). The securing means includes a temporary thread (476). The housing also has a central axis 479 and a coupling section 510.

301A is an enlarged view of FIG. The cylinder 470 has a cylinder wall portion 511 having a diameter suitable for the piston ring 508 of the piston 477. The cylinder wall includes enlarged wall portions 475a, 475b, 476a which include flow channel portions 471, 472, 473 around the piston means 477, 508 when the actuating pin sufficiently opens the valve core, Is included in its first end vicinity 492. Now, the flow from the pressure source to the valve can be established. Here, the first end 492 of the cylinder 470 functions as a stop for the movement of the actuating pin. The channel portions 473 and 474 are part of the piston control means 476c. For example, these portions may have a variety of shapes depending on the selected manufacturing technique: for example, channel portions 473 and 474 are part of a circle, channel portion 507 is made by injection molding as a cylinder, The channel portion 507 may be a perforated hole. The channel portions 473 and 474 can be regarded as being 'flow formed' and are configured to reduce air resistance. The inclined enlarged wall portion 475a forms an angle τ with the central axis 479 which is greater than 0 ° and less than 20 ° and which is generally perpendicular to the direction of the gas phase and / Which is in the range of 1 ° <τ <12 °. The piston control means 476c has three grooves with walls 476a and 476b, respectively. The wall 476a forms an angle, [omega], greater than 0 [deg.] And less than 20 [deg.] (Typically in the range of 6 [deg.] To 12 [deg.]) With respect to the direction of the gas and / If the piston control does not have a groove, the channel 507 is an alternative to the channel portions 473 and 474 described above. In this alternative example, a hole 507 parallel to the center axis 479 by the piston control connects the coupling hole with the channel portion 475b (shown by two dotted lines).

Fig. 301B shows the section G-G from Fig. 301A together with the channel portions 473 and 474 and the stopper 492. Fig. An alternative channel portion 507 is shown in phantom.

302 includes a first annular portion 482 and a second annular sealing portion 483 disposed coaxially with the central axis 486 of the coupling section in the direction of the central axis 486 of the coupling section 503 A valve actuator in a universal clip-on valve connector with a sealing means and a housing 504. The first annular sealing portion 482 is closer to the opening 502 of the coupling section than the second annular sealing portion 483 and the diameter of the first annular sealing portion 482 is smaller than the diameter of the second annular sealing portion 483 It is bigger than diameter. The coupled valves may be secured by at least one 'clip' (ie, temporary thread) 476. However, two clips 493 facing each other are preferred. The taper cone 501 near the sealing surface 482 helps valve centering. The taper cone forms an angle? With the central axis 486, and generally this angle is greater than 45 degrees. A separate cylinder sleeve 496 with a cylinder wall portion 509 is shown sealed. The cylinder sleeve is secured within the wall of the housing 504, for example, with a snap-lock 497. This is an economical way to enable the negative slip angle of the sloping enlarged wall portion 512. The cylinder sleeve 496 is spaced at an angle (?) From the piston stop 495 such that the piston ring 508 is not sealed.

Figure 302a shows channel portions 480 and 481 respectively formed by enlarged wall portions 487 and 488 of the piston control means. The actuating pin is simplified by the piston 484 and the piston rod 485. The wall portion 487 forms an angle (κ) greater than 0 ° and less than 20 ° (typically in the range of 6 ° to 12 °) with respect to the central axis 486 when viewed in the direction of the medium coming from the pressure source. The stepped surface 498 of the wall of the housing 504 is hermetically connected from the wall of the cylinder sleeve 496 to the cylinder 499. It is of course possible to airtightly connect to the other side of the cylinder. At the lower end of the cylinder sleeve 496 is shown an inclined enlarged wall portion 512 which forms a channel portion 471 with a piston ring 515.

Fig. 302B shows a section G-G of Fig. 302A together with a stopper 495 for movement of the operating pin. Wall portion 488 and channel portion 481 are also shown.

FIG. 303 shows an operation pin similar to the pin of FIG. A piston 529 is also shown. The piston rod 531 need not be sealed to the piston control portion.

A cylinder 536 of the valve actuator is disposed within the housing 532 of the valve connector.

Coupling section 530 is also shown.

Figure 303a shows a channel portion 533 with a radial perforation 534 and a channel portion 533 with an extension 535. [ The piston ring 539 opens and closes this conduction channel in its orifice 537 depending on the position of the actuating pin. The direction of the channel portion 534 with respect to the central axis is similar to the angle? Of the channel portion 471 of FIG. The wall of the extension 535 has an angle similar to the angle omega of the wall 476a of FIG. The cylinder wall portion 538 of the cylinder 536 is also shown.

Figure 304 shows the actuating pin and its cylinder shown in Figure 301. This pin is formed in the interior of the assembled pipeline housing means 520 and 521 and a valve 522 with a core pin 523 actuated by a spring force is provided inside the housing means, . The actuating pin engages the core pin 523 of the valve.

Figure 305 shows a valve actuator in a universal valve connector. This is similar to that shown in FIG. However, it is possible to seal two valves of different sizes, spaced apart by a distance A. In the cylinder wall 550, two enlarged portions 1 and 2 of the diameter of the cylinder 542 are shown separated by a distance B. The actuating pin 543 is also shown with two engagement levels on the distance B. May be the same or different, for example, if the types of valves are different, the distance from the core pin to the seal is not the same. Between the two enlarged portions 1 and 2 there is a cylindrical wall portion 544 with a cylinder portion 545 that fits into the piston ring 508. The center axis 546, the coupling section 547, and its opening 548 from the housing 459 are also shown,

19597 Description of the preferred embodiment

Figure 401a shows the XX line between two mating surfaces 1, 2 of the three mating surfaces of the hard surface 5 and the base 4, can do. Y-Y lines are present between the two coupling surfaces 2, 3 of the three coupling surfaces of the hard surface 5 and the base 4, and the combination 6 can move around this line. There is a Z-Z line between two contact points 1, 2 out of the three contact points of the hard surface 5 and the base 4, and the combination 6 can move around this line.

401b shows a combination body 6 including a chamber 7, a guide 8 for a piston rod 9, and a handle 10. Fig. The base 4 has rounded contact points 1, 2 and 3 towards the hard surface. The chamber (7) is rigidly connected to the base (4) by a reinforcement (11).

Figure 402a shows the handle 10 of the combination 6 when the combination 6 is in the rest position 12.

Figure 402b shows the combination 6 in the rest position 12 when the transition 13 between the combination 6 and the stiffener 14 of the base 40 is in the rest position. The transition portion 13 can be made of a flexible material and is disposed around the chamber 7.

Figure 402c shows the activated position 14 of the handle 10 when the handle 10 has moved forward from its rest position 12 to the rest position.

Figure 402d shows the activated position 15 of the handle 10 when the handle has moved back from its rest position 12 to the rest position.

Figure 402e shows the activated position 16 of the handle 10 when the handle has moved from its rest position 12 to the left front of the rest position.

Figure 402f shows the activated position 17 of the handle 10 when the handle has moved from its rest position 12 to the left rear position of the rest position.

Figure 402g shows the activated position 18 of the handle 10 when the handle has moved from its rest position 12 to the right front of the rest position.

Figure 402h shows the activated position 19 of the handle 10 when the handle has moved from its rest position 12 to the right rear of the rest position.

Figure 403a shows a floor pump in which the transition between the chamber 7 and the base 4 is a resiliently deformable bushing 20.

Figure 403b shows an enlarged view of the transition between the chamber 7 and the base 40. [ The chamber 7 has a protrusion 21 which coincides with the groove 22 in the bushing 20 so as to simplify the mounting of the chamber 7 in the base 40. A protrusion 41 is formed on the upper end of the reinforcing member 42 of the base 40.

Figure 403c shows a floor pump in which the transition between the chamber 7 and the base 4 is a resiliently deformable bushing 23.

403d shows an enlarged view of the transition between the chamber 7 and the base 40. Fig. The chamber 7 has a groove 25 coinciding with the projection 24 in the bushing 23 so that the mounting of the chamber 7 in the base 40 can be simplified.

Figure 404a shows a floor pump type combination 6 with a cap 25 to allow lateral translation and / or deflection of the piston rod relative to the base 43 and the rest of the combination 6. The base 43 may be connected directly, using a stiffener 42, or indirectly, e.g., using a flexible bushing connected to the base 41.

Figure 404b shows an enlarged view of the cap 25 of Figure 404a when the piston 44 is at the end of the stroke furthest from the base 43. [ The piston rod 9 is moving in the guide means 26 and the convex contact inner surface 31 of the guide means comes into line contact with the piston rod 9 at the center line 27 thereof. The guiding means 26 is held inside the cap 9 by the surfaces 36, 37 and the flexible O-ring 28. The cross sectional area of the space 29 between the guiding means 26 and the surfaces 36 and 37 of the cap 9 is larger than the cross sectional area of the ring 28 itself so as to enable significant compression of the ring 28. [ (See FIG. 404C, for example). A distance a exists between the wall 38 of the spaces 33 and 34 of the cap 9 and the outside of the piston rod 9. The distance may be approximately equal to the distance b between the wall 38 of the cap 9 at the top of the cap and the piston rod.

Figure 404c shows Figure 4b in which the central axis 32 of the piston rod 9 'is deflected by an angle a relative to the remaining central axis 30 of the combination. The space 29 'is almost filled with a compressed ring 28' which is compressed by the translating guide means 26 '. The space 34 'is shown. The space 33 'is shown. There is a contact surface 35 between the guide means 26 'and the piston rod 9'. The distance a 'is smaller than the distance a in FIG.

The distance b 'is smaller than the distance b in Figure 404b and is greater than the difference between the distances a, a'.

Figure 404d shows an enlarged view of the cap 25 of Figure 404a when the piston 44 may be at the end of the stroke closest to the base 43. [ The centerline 30 of the combination is shown. There is a space 33, 34 between the piston rod 9 and the inner wall 38 of the cap 25.

Figure 404e shows Figure 404d when the piston rod 9 'translates to the left with a distance "a" between the inner wall 38 of the cap 9 and the outside of the piston rod 9' The guide means 26 "compresses the ring 28" and moves to the left, with the space 29 "filled with the compressed ring 28 "Quot; is substantially equal to space 34 ", and distance a "is equal to distance b" which is less than distance a.

Figure 405a shows the left portion 51 of the handle 52 and the right portion 53 of the handle 52 with respect to the center axis 54 of the combination 55. The angle alpha between the central axis 56 of the left portion 51 of the handle 52 and the center axis 57 of the right portion 53 of the handle 52 Lt; / RTI &gt; The center point 61 of the left portion 51 and the center point 62 of the right portion 53 are shown.

Fig. 405b shows a front view of the floor pump of Fig. 5a including a handle 52 and a combination 55. Fig. The handle 52 has a left portion 51 and a right portion 53. The center axis 54 of the combination 55 is shown.

Figure 406a shows the left portion 58 of the handle 59 and the right portion 60 of the handle 59 with respect to the central axis 54 of the combination 55. The angle alpha between the central axis 56 of the left portion 58 of the handle 59 and the center axis 61 of the right portion 60 of the handle 59 as viewed from the user's position X is &Lt; / RTI &gt;

Figure 406b shows a front view of the floor pump of Figure 406a including handle 59 and combination 55. [ The handle 59 has a left portion 58 (= rotated right portion 53) and a right portion 60 (= rotated left portion 51).

507 Summary of invention

The valve actuator of the present invention and its embodiments are the subject matter of claims 1, 2 to 17. The valve connector and the pressure vessel or the hand pump including the valve actuator of the present invention are the subjects of claims 18 and 19, respectively. Claim 20 relates to the use of a valve actuator in a stationary structure.

The present invention provides a valve actuator including an actuating pin having a simple structure and an inexpensive cylinder combination in which a piston for driving the actuating pin moves. This combination can be used not only in the valve connector (e.g., to inflate an automobile tire) but also in a stationary structure such as a chemical plant where the actuating pin engages a spring force of a spring (e.g., a release valve) of a core pin. The disadvantages of the conventional valve connector can be overcome by the valve actuator of the present invention. The valve actuator features a piston with a piston ring fitted to the cylinder, the piston being disposed at a first predetermined distance from the first end of the cylinder in the first position. The piston is disposed at a second predetermined distance from the first end of the cylinder in the second position and the predetermined second distance is greater than the predetermined first distance. The cylinder wall includes a conduction channel that allows conduction of gas phase and / or liquid phase media between the cylinder and the coupling section when the piston is in the first position, while conduction of the gas phase and / or liquid phase medium between the cylinder and the coupling section And is inhibited by the piston when the piston is in the second position.

An embodiment of the actuating actuator of the invention according to claim 6 is characterized in that the conduction channel from the pressure source to the valve to be actuated comprises an enlarged portion of the cylinder diameter arranged around the piston of the actuating pin at the lower end of the cylinder, When in the first position, the medium from the pressure source is allowed to flow, for example, from the shrouder valve to the valve core pin actuated by an open spring force. The cylinder diameter enlarging portion may be uniform or the cylinder wall may include one or a plurality of sections in the vicinity of the lower end of the cylinder so that when the piston is in the first position the gas phase and / The distance between the centerline of the cylinder and the cylinder wall increases so that it can flow freely. The modification of this embodiment has a valve actuator arrangement in which the enlarged diameter of the cylinder is doubled. The distance between the enlarged portions may be equal to the distance between the sealing levels of the sealing means. When three valves of different sizes can be coupled, the valve actuator may include a cylinder with three enlargements. However, it is also possible to connect valves of different sizes to valve actuators having a single arrangement for an enlarged portion of the cylinder diameter. Thus, now the number of enlarged portions can be different from the number of different valve sizes of the valves that can be coupled.

Another embodiment of the invention according to claim 10 features a conduction channel through a portion of the body of the valve actuator. The channels form passages for gaseous and / or liquid mediums between the part of the valve actuator coupled to the valve and the cylinder. The orifices of the channel openings in the cylinder are arranged such that when the piston is in the first position, the pressurized gaseous and / or liquid mediums flowing from the pressure source to the cylinder can further flow to the valve to be actuated through the channel. When the piston is in the second position, the piston blocks the cylinder so that pressurized gaseous and / or liquid mediums can not flow into the channel.

When the piston is in the first position, instead of air, any mixture of gases and / or liquids can actuate the actuating pin and flow around the piston of the valve actuator. The present invention can be applied to all types of valve connectors to which a valve (e.g., a shrouder valve) having a spring force-actuated core pin can be coupled, regardless of the coupling method or the number of coupling holes in the connector . In addition, the valve actuator can be integrated into any pressure source (e.g., a hand pump or pressure vessel), regardless of the availability of the fastening means in the valve connector. The present invention can be used in a permanent structure where the actuating pin of the actuator engages the core pin of the permanently mounted valve.

The various embodiments described above are provided by way of example and are not to be construed as limiting the invention. It will be apparent to those skilled in the art that various modifications and variations can be made in the present invention without departing from the true spirit and scope of the invention as claimed and without departing from the spirit and scope of the present invention as defined by the following claims. It will be easy to understand.

Claims (151)

A chamber (162, 186, 231) defined by an inner chamber wall (156, 185, 238) and at least a first longitudinal position and a second longitudinal position, A piston-chamber combination comprising an actuator piston in a chamber,
Wherein the chamber has a cross-section of a circumferential length that is different from the cross-sectional area at the first longitudinal position and the second longitudinal position, and wherein the chamber is at least substantially continuously different in an intermediate longitudinal position between the first longitudinal position and the second longitudinal position Sectional area and circumferential length at the first longitudinal position being smaller than the cross-sectional area and circumferential length at the first longitudinal position,
Wherein the actuator piston has a different cross-sectional area of the piston, which is adapted to a circumferential length different from the different cross-sectional area of the chamber during relative movement of the piston between the first longitudinal position and the second longitudinal position through the mid- And includes elastically deformable containers 208, 208 ', 217, 217', 228, 228 ', 258, 258', 450, 450 'to provide a circumferential length,
The actuator pistons are in a non-stressed, unstrained state in which the circumferential length of the piston is approximately equal to the circumferential length of the chamber (162, 186, 231) at the second longitudinal position, , 217 ', 228, 228', 258, 258 ', 450, 450'), the container being inflatable from a manufacturing dimension transverse to the longitudinal direction of the chamber, such that the actuator piston Providing an expansion of the piston from the manufacturing dimensions when relative movement from the second longitudinal position to the first longitudinal position,
The containers 208, 208 ', 217, 217', 228, 228 ', 258, 258', 450, 450 'are resiliently deformable to provide different cross-sectional areas and circumferential lengths of the actuator pistons, In this case,
The combination comprising means for introducing fluid from a position external to the container into the container to enable pressurization of the container and to expand the container,
Wherein the smooth surface of the wall of the actuator piston continues to at least proximate the area of contact with the wall of the chamber thereby displacing the vessel from the second longitudinal position to the first longitudinal position of the chamber.
Piston-chamber combination. A chamber (162, 186, 231) defined by an inner chamber wall (156, 185, 238) and at least a first longitudinal position and a second longitudinal position, A piston-chamber combination comprising an actuator piston in a chamber,
Wherein the chamber has a cross-section of a circumferential length that is different from the cross-sectional area at the first longitudinal position and the second longitudinal position, and wherein the chamber is at least substantially continuously different in an intermediate longitudinal position between the first longitudinal position and the second longitudinal position Sectional area and circumferential length at the first longitudinal position being smaller than the cross-sectional area and circumferential length at the first longitudinal position,
Wherein the actuator piston has a different cross-sectional area of the piston, which is adapted to a circumferential length different from the different cross-sectional area of the chamber during relative movement of the piston between the first longitudinal position and the second longitudinal position through the mid- And includes elastically deformable containers 208, 208 ', 217, 217', 228, 228 ', 258, 258', 450, 450 'to provide a circumferential length,
The actuator pistons are in a non-stressed, unstrained state in which the circumferential length of the piston is approximately equal to the circumferential length of the chamber (162, 186, 231) at the second longitudinal position, , 217 ', 228, 228', 258, 258 ', 450, 450'), the container being inflatable from a manufacturing dimension transverse to the longitudinal direction of the chamber, such that the actuator piston Providing an expansion of the piston from the manufacturing dimensions when relative movement from the second longitudinal position to the first longitudinal position,
The containers 208, 208 ', 217, 217', 228, 228 ', 258, 258', 450, 450 'are resiliently deformable to provide different cross-sectional areas and circumferential lengths of the actuator pistons, A piston-chamber combination comprising:
The combination comprising means for permitting pressurization of the container and for expanding the container by varying the volume of the enclosed space in communication with the actuator piston of the container from a position external to the container,
Wherein the smooth surface of the wall of the actuator piston continues to at least proximate the area of contact with the wall of the chamber thereby displacing the vessel from the second longitudinal position to the first longitudinal position of the chamber.
Piston-chamber combination. 3. The method according to claim 1 or 2,
The actuator piston being sealably movable with respect to the chamber wall within or outside the chamber,
Piston-chamber combination. The method according to claim 1, 2, or 3,
Wherein a portion of the chamber disposed adjacent the actuator piston communicates with the chamber through a channel or through the atmosphere,
Piston-chamber combination. 5. The method according to any one of claims 1 to 4,
Wherein the chamber is elongated,
Piston-chamber combination. 5. The method according to any one of claims 1 to 4,
The chamber may be circular,
Piston-chamber combination. The method according to claim 6,
The chamber is formed around a central axis of circular motion,
Piston-chamber combination. 8. The method according to any one of claims 1 to 7,
Wherein the actuator piston is depressurized to not engage the wall of the chamber,
Piston-chamber combination. 9. The method of claim 8,
Wherein the piston moves from a first longitudinal position to a second longitudinal position of the chamber,
Piston-chamber combination. 8. The method according to any one of claims 1 to 7,
A portion of the length of the wall of the chamber being parallel to the central axis of the chamber,
Piston-chamber combination. 11. The method of claim 10,
The wall of the chamber being disposed at the end of the stroke of the actuator piston,
Piston-chamber combination. 8. The method according to any one of claims 1 to 7,
The containers 208, 208 ', 217, 217', 228, 228 ', 258, 258', 450, 450 'include deformable materials 205,
Piston-chamber combination. 13. The method of claim 12,
The deformable material 205, 206 may be a fluid or fluid mixture, such as water, steam, and / or gas,
Piston-chamber combination. The method according to claim 12 or 13,
In a cross-section passing through the longitudinal direction, the container when positioned in the first longitudinal position of the chamber (186, 231) is different from the second shape of the container when positioned in the second longitudinal position of the chamber A first shape,
Piston-chamber combination. 15. The method of claim 14,
At least a portion of the deformable material (206) being compressible, the first shape having an area greater than an area of the second shape,
Piston-chamber combination. 15. The method of claim 14,
The deformable material (206) is at least substantially incompressible,
Piston-chamber combination. 8. The method according to any one of claims 1 to 7,
The container includes an inflatable,
Piston-chamber combination. 8. The method according to any one of claims 1 to 7,
The container (208, 208 ', 217, 217', 228, 228 ', 258, 258', 450, 450 ') further comprises a sealed space (210, 243)
Piston-chamber combination. 19. The method of claim 18,
Wherein the introduction of fluid from a position outside the container into the container is through a first enclosure communicating with the enclosure,
Piston-chamber combination. 8. The method according to any one of claims 1 to 7,
Further comprising means for enabling contraction of said vessel by removing fluid from said vessel to a position external to said piston,
Piston-chamber combination. 21. The method of claim 20,
Wherein the fluid is removed through a second closed space communicating with the closed space,
Piston-chamber combination. The method according to any one of claims 2 to 7 or 18,
Wherein the means is adapted to vary the volume of the enclosed space and to reduce the pressure of the actuator piston by increasing the volume to enable contraction of the container by communicating with the enclosed space of the piston,
Piston-chamber combination. 23. The method of claim 22,
The piston being moveable relative to the chamber from a first longitudinal position to a second longitudinal position of the chamber,
Piston-chamber combination. 8. The method according to any one of claims 1 to 7,
The walls of the vessels 208, 208 ', 217, 217', 228, 228 ', 258, 258', 450, 450 '
Piston-chamber combination. 6. A method according to any one of the preceding claims,
Wherein the cross-section of the wall of the chamber and the contact surface of the container is such that, on the second longitudinal position side, it cuts the central axis of the container in the longitudinal direction substantially next to the midpoint of the section of the resiliently deformable wall of the container ,
Piston-chamber combination. 26. The method of claim 25,
Wherein the cross-section of the wall of the chamber and the contact surface of the container is such that, on the second longitudinal position side, it cuts the central axis of the container longitudinally about the center of the section of the resiliently deformable wall of the container,
Piston-chamber combination. The method according to claim 12, 17, 20, or 22,
Wherein the actuator piston comprises a piston rod, the piston rod including the enclosed space,
Piston-chamber combination. 27. The method of claim 26,
Wherein the piston rod comprises a coupling means outside the chamber,
Piston-chamber combination. 29. The method of claim 28,
Further comprising a crank configured to convert the motion of the piston between the second and first longitudinal positions of the chamber into rotation of the crank,
Piston-chamber combination. 29. The method of claim 28,
The crank converting its rotation into piston motion from a first longitudinal position to a second longitudinal position of the piston,
Piston-chamber combination. 28. The method of claim 19, 21 or 28,
Wherein the crank includes the first and second closed spaces,
Piston-chamber combination. 8. The method according to any one of claims 1 to 7,
Wherein the cross-sectional area of the chamber at the second longitudinal position is between 95% and 15% of the cross-sectional area of the chamber at the first longitudinal position.
Piston-chamber combination. 8. The method according to any one of claims 1 to 7,
Wherein the cross-sectional area of the chamber at the second longitudinal position is approximately 50% of the cross-sectional area of the chamber at the first longitudinal position,
Piston-chamber combination. 8. The method according to any one of claims 1 to 7,
Wherein the cross-sectional area of the chamber at the second longitudinal position is approximately 5% of the cross-sectional area of the chamber at the first longitudinal position.
Piston-chamber combination. The method according to any one of claims 1 to 6,
The chamber includes convexly shaped walls of longitudinal cross-sectional sections adjacent a first longitudinal position, the sections being divided from one another by a common boundary, and the distance between two subsequent common boundaries is defined by the longitudinal cross- Wherein the height is reduced by increasing the overpressure ratio of the actuator piston to the pressure in the chamber and the transverse length of the cross-sectional common boundaries is greater than the transverse length of the actuator pistons Lt; RTI ID = 0.0 &gt;
Piston-chamber combination. The method according to any one of claims 1 to 6,
The chamber includes convexly shaped walls of longitudinal cross-sectional sections adjacent a first longitudinal position, the sections being divided from one another by a common boundary, and the distance between two subsequent common boundaries is defined by the longitudinal cross- Wherein the height decreases from a first longitudinal position to a second longitudinal position and a lateral length of the cross-sectional common boundaries is greater than a maximum actuating force of the actuator pistons constantly selected with respect to the common boundaries Lt; / RTI &gt;
Piston-chamber combination. 37. The method of claim 35 or 36,
Wherein the chamber further comprises a wall parallel to the central axis of the chamber,
Piston-chamber combination. The method according to any one of claims 35 to 37,
Wherein the chamber further comprises a concave shaped wall,
Piston-chamber combination. 39. The method of claim 38,
The chamber further comprising a transition between the convexly shaped wall and the parallel wall, the transition comprising a concave shaped wall,
Piston-chamber combination. As a shock absorber,
39. A combination according to any one of claims 1 to 39,
And coupling means coupled to the piston from a position external to the chamber,
The coupling means having an outer position in which the piston is in a first longitudinal position of the chamber and an inner position in which the piston is in a second longitudinal position,
Shock absorber. 41. The method of claim 40,
Further comprising a sealed space in communication with said container,
Shock absorber. 42. The method of claim 41,
The closed space has a variable volume,
Shock absorber. 42. The method of claim 41,
The closed space has a constant volume,
Shock absorber. 42. The method of claim 41,
The enclosed space may comprise an adjustable,
Shock absorber. 45. The method according to any one of claims 41 to 44,
Wherein the container and the enclosure define at least a substantially sealed cavity comprising a fluid and the fluid is compressed as the piston moves from a first longitudinal position to a second longitudinal position of the chamber,
Shock absorber. A pump for pumping fluid,
39. A composition according to any one of claims 1 to 39,
Means for coupling to a second piston in a second chamber from a location outside said chamber,
A fluid inlet coupled to the second chamber and including valve means,
And a fluid outlet connected to the second chamber.
Pump. A pump for pumping fluid,
39. A composition according to any one of claims 1 to 39,
Means for engaging a piston in the chamber from a position outside the chamber;
A fluid inlet coupled to the chamber and including valve means,
And a fluid outlet coupled to the chamber.
Pump. 46. The method according to claim 46 or 47,
The coupling means having an external position in which the piston is in a first longitudinal position of the chamber and an internal position in which the piston is in a second longitudinal position of the chamber,
Pump. 46. The method according to claim 46 or 47,
The coupling means having an outer position in which the piston is in a second longitudinal position of the chamber and an inner position in which the piston is in a first longitudinal position,
Pump. Use of a piston-chamber combination according to any one of claims 1 to 3 in a motor, in particular an automotive motor. In the motor,
A piston-chamber assembly as claimed in any one of the preceding claims,
motor. In the motor,
A piston-chamber assembly according to claim 2,
motor. 51. The method according to any one of claims 1, 3, 4, 5, 6, 7, 8, 9, 10,
Wherein the crankshaft includes a second closed space in which one end communicates with an external pressure source and the other end communicates with a closed space of the actuator piston,
motor. 54. The method of claim 53,
Wherein the crankshaft includes a third enclosed space in communication with the enclosed space of the actuator piston and the other end communicating with the re-pressurizing pump, the re-pressurizing pump communicating with the electric motor, Such as a fuel cell, such as a fuel cell, or an alternator in communication with the main shaft,
motor. 55. The method of claim 54,
The alternator is connected to an axis of an auxiliary power source, such as a combustion motor for burning oxygen in the air and hydrogen obtained by electrolyzing conductive water coming from an outside-
motor. 55. The method of claim 54,
The last mentioned pump communicates with the axes of the auxiliary power source, such as the hydrogen obtained by electrolyzing the conductive water from the tank that can be filled from the outside and the combustion motor burning the oxygen in the air,
motor. 54. The method of claim 53,
Wherein communication between the pressure source and the enclosed space of the actuator piston occurs at a portion of each crankshaft rotation,
motor. 55. The method of claim 54,
The communication between the closed space of the piston and the repressurization cascade occurs at a portion of each crankshaft rotation,
motor. 58. The method of claim 57,
Wherein the channels are separated in time from each other,
motor. 60. The method of claim 59,
Said communication being effected by a T-shaped valve controlled by a computer in electrical communication with the main shaft of said motor,
motor. 64. The method of claim 60,
Wherein the pressure and / or volume of the supply channel for the T-shaped valve is controlled by a pressure reducing valve, the pressure reducing valve being controlled by a speeder,
motor. 62. The method of claim 61,
Wherein the pressure reducing valve communicates with the pressure storage vessel and the pressure storage vessel communicates with the re-pressurized cascade of the pumps, and at least one pump of the pumps communicates with the main shaft of the crankshaft (via the other crankshaft) Wherein the at least one pump is in communication with an electric motor and wherein the motor obtains energy from a battery charged by an energy source such as a fuel cell such as a solar or hydrogen fuel cell or an alternator in communication with the main axis,
motor. 63. The method of claim 62,
The alternator is connected to an axis of an auxiliary power source, such as a combustion motor for burning oxygen in the air and hydrogen obtained by electrolyzing conductive water coming from an outside-
motor. 64. The method of claim 63,
The last mentioned pump communicates with the axes of the auxiliary power source, such as the hydrogen obtained by electrolyzing the conductive water from the tank that can be filled from the outside and the combustion motor burning the oxygen in the air,
motor. 65. The method of claim 62,
The pumps are piston pumps or rotary pumps,
motor. 39. The method according to any one of claims 2 to 39, 46 to 51,
Wherein the enclosed space, the second enclosed space, and the third enclosed space form a closed cavity,
motor. 67. The method of claim 66,
Wherein the pressure in the cavity is controlled by a piston-chamber combination in communication with a bidirectional piston-chamber combination, the bidirectional piston-chamber combination being controlled by a speed-
motor. 68. The method of claim 67,
Wherein the bi-directional actuator piston-chamber combination communicates with a pressure vessel, the vessel communicates with a repressurizing cascade of pumps, and at least one of the pumps is connected to a main shaft (of the crankshaft via another crankshaft) While at least one pump is in communication with the electric motor and the motor is driven by an energy source such as solar heat and / or by electricity from a fuel cell such as a hydrogen fuel cell, or alternatively by an alternator To obtain energy from a battery to be charged by the battery,
motor. 69. The method of claim 68,
The last mentioned pump includes a tank that can be filled and, if necessary, directly connected to the axis of an auxiliary power source, such as hydrogen, obtained by electrolysis of the conductive water coming from the conductive means storage tank, and a combustion motor, ,
motor. 70. The method of claim 67,
Wherein the pressure in said cavity is additionally controlled by a piston-chamber combination in communication with said pressure vessel,
motor. 66. The method of claim 65,
The pressure in the closed cavity of the piston is controlled electrically by a computer, by a piston-chamber combination in communication with the main shaft of the motor,
motor. 66. The method of claim 65,
Wherein the pressure in the closed cavity of the piston is controlled by a piston-chamber combination communicating with the main shaft of the motor via a cam wheel in communication with the camshaft,
motor. The method of claim 61 or 70,
The pumps are piston pumps or rotary pumps,
motor. The method according to any one of claims 1 to 4 and 6 to 73,
Wherein the piston rotates about a central axis of the chamber,
motor. The method according to any one of claims 1 to 4 and 6 to 73,
Wherein the chamber rotates,
motor. 75. The method of claim 74 or 75,
Wherein the piston and the chamber rotate,
motor. 76. The method of claim 74,
The actuator piston-chamber combination comprises at least two sub-chambers comprising an actuator piston, wherein the sub-chambers are arranged in series with one another so that the first circular portion of the sub- Adjacent to the circular portion,
motor. 78. The method of claim 77,
The sub-
motor. 79. The method of claim 78,
Each sub-chamber comprising an actuator piston, the pistons being identical, each piston being disposed in a different circular position relative to one another in the sub-chamber,
motor. 79. The method of claim 74,
The shape of the piston is such that, during the stroke,
motor. 69. The method of claim 62 or 68,
Wherein the pressure vessel is pressurized by an external pressure source through a connectable connection,
motor. The method of claim 54, 62 or 68,
Wherein the battery is charged by an external power source through a connectable connector,
motor. (70) defined by an inner chamber wall (71, 73, 75), and at least a second longitudinal position between the first longitudinal position and the second longitudinal position of the chamber A piston-chamber combination comprising piston means (76, 76 ', 163)
Wherein the chamber has a cross-section of a different cross-sectional area at a first longitudinal position and a second longitudinal position of the chamber, and at least substantially continuously different cross-sectional areas at an intermediate longitudinal position between the first longitudinal position and the second longitudinal position, Wherein the cross-sectional area at the first longitudinal position is greater than the cross-sectional area at the second longitudinal position,
Wherein the piston means is adapted to pass through the intermediate lengthwise position of the chamber and, during relative movement of the piston means from a first longitudinal position to a second longitudinal position, In a piston-chamber combination designed to be controlled,
The piston means 76, 76 ', 163, 189 and 189' comprise a plurality of at least substantially rigid support members 81, 82 and 184 rotatably coupled to a common member 6, 23, 45 and 180, Lt; / RTI &gt;
The support member is provided in an elastically deformable means 79 supported by the support member for sealing against the inner walls 71, 73, 75, 155, 156, 157, 158 of the chamber 70 ,
The support member is rotatable about 10 to 40 degrees with respect to the longitudinal axis 19 of the chamber 70,
Characterized in that the support members (81, 82, 184) are inflatable.
Piston-chamber combination. 85. The method of claim 83,
The piston being sealably movable with respect to the chamber wall either inside or outside the chamber,
Piston-chamber combination. 85. The method of claim 83,
Wherein the support member has a predetermined bending force,
Piston-chamber combination. 85. The method of claim 83,
The support member (81, 82, 184) is rotatable at least approximately parallel to the longitudinal axis (19)
Piston-chamber combination. 85. The method of claim 83,
The elastically deformable means (79) are made of polyurethane foam,
Piston-chamber combination. 88. The method of claim 87,
Wherein the polyurethane foam comprises a polyurethane memory foam and a polyurethane foam,
Piston-chamber combination. 90. The method of claim 88,
The polyurethane foam can be made from most polyurethane memory foam and some polyurethane foam,
Piston-chamber combination. 87. The method of claim 87,
Said polyurethane foam comprising a flexible impermeable membrane,
Piston-chamber combination. 89. The method of claim 90,
Wherein said impermeable membrane has a fabrication size in a non-stressed state in which its circumference is approximately equal to the circumference of said chamber wall in a second longitudinal or circular position,
Piston-chamber combination. 83. The method of claim 83 or 86,
The common member being attached to the crankshaft,
Piston-chamber combination. 90. The method of claim 83 or 88,
The common member is attached to a piston-chamber combination, which is an external bi-directional actuator.
Piston-chamber combination. (70) defined by an inner chamber wall (71, 73, 75), and at least a second longitudinal position between the first longitudinal position and the second longitudinal position of the chamber A piston-chamber combination comprising piston means (76, 76 ', 163)
Wherein the chamber has a cross-section of a different cross-sectional area at a first longitudinal position and a second longitudinal position of the chamber, and at least substantially continuously different cross-sectional areas at an intermediate longitudinal position between the first longitudinal position and the second longitudinal position, Wherein the cross-sectional area at the first longitudinal position is greater than the cross-sectional area at the second longitudinal position,
Wherein the piston means is adapted to pass through the intermediate lengthwise position of the chamber and, during relative movement of the piston means from a first longitudinal position to a second longitudinal position, In a piston-chamber combination designed to be controlled,
The piston means 49 and 49 'comprise a plurality of at least substantially rigid support members 43 rotatably coupled to the piston rod 45 by a shaft 44,
The support member is supported by a sealing means 41 supported by a spring 42 for sealing against the inner walls 71, 73, 75, 155, 156, 157, 158 of the chamber 70,
The support member is rotatable by 1 DEG to 2 DEG with respect to the longitudinal axis 19 of the chamber 70,
A flexible impermeable film (sheet) 40 is mounted in the sealing means (O-ring) 41 so as to be disposed perpendicular to the central axis 19 of the chamber 1,
The film (flexible impermeable sheet) comprises a reinforcing layer,
Characterized in that the support member (means), the sealing means (O-ring), the flexible impermeable film (sheet) and the spring (arranged)
Piston-chamber combination. 95. The method of claim 94,
The support member (means) 81, 82, 184 is rotatable at least approximately parallel to the longitudinal axis 19,
Piston-chamber combination. 95. The method of claim 94,
Wherein the flexible reinforcing layer (sheet) comprises a helical stiffener,
Piston-chamber combination. 95. The method of claim 94,
Wherein the stiffening layer (sheet) comprises a stiffener shaped in a concentric arrangement about a central axis of the chamber,
Piston-chamber combination. 95. The method of claim 94,
Wherein the flexible impermeable membrane (sheet) is at an angle greater than &lt; RTI ID = 0.0 &gt; 90 with &lt; / RTI &
Piston-chamber combination. 98. The method of claim 98,
The flexible impermeable film (sheet) is mounted on the piston rod,
Piston-chamber combination. 98. The method of claim 98,
Wherein the flexible impermeable film (sheet) is formed by vulcanizing on the piston rod,
Piston-chamber combination. 95. The method of claim 83 or 94,
The common member includes a piston-
Piston-chamber combination. 95. The method of claim 94,
The flexible impermeable sheet is supported by a foam,
Piston-chamber combination. 103. The method of claim 102,
The foam being reinforced by a rigid member rotatably coupled to the piston rod,
Piston-chamber combination. A chamber (162, 186, 231) defined by an inner chamber wall (156, 185, 238) and at least a first longitudinal position and a second longitudinal position, A piston-chamber combination comprising a piston means in a chamber,
Wherein the chamber has a cross-section of a circumferential length that is different from the cross-sectional area at the first longitudinal position and the second longitudinal position, and wherein the chamber is at least substantially continuously different in an intermediate longitudinal position between the first longitudinal position and the second longitudinal position Sectional area and circumferential length at the first longitudinal position being smaller than the cross-sectional area and circumferential length at the first longitudinal position,
Wherein the piston means comprises a piston having a different cross-sectional area of the piston, preferably in a circumferential length different from the different cross-sectional area of the chamber during a relative movement of the piston between a first longitudinal position and a second longitudinal position, And includes elastically deformable containers 208, 208 ', 217, 217', 228, 228 ', 258, 258', 450, 450 'to provide a circumferential length,
The piston means is adapted to move in a non-stressed, unstrained state in which the circumferential length of the piston is approximately equal to the circumferential length of the chamber (162, 186, 231) at the second longitudinal position, , 217 ', 228, 228', 258, 258 ', 450, 450'), the container being inflatable from a manufacturing dimension transverse to the longitudinal direction of the chamber, such that the actuator piston Providing an expansion of the piston from the manufacturing dimensions when relative movement from the second longitudinal position to the first longitudinal position,
The containers 208, 208 ', 217, 217', 228, 228 ', 258, 258', 450, 450 'are resiliently deformable to provide different cross-sectional areas and circumferential lengths of the actuator pistons, In this case,
The piston means 92, 92 ', 146, 146', 168, 168 ', 208, 208', 222, 222 ' , 173, 173 ', 174, 174', 205, 205 ', 206, 206', 215, 215 ', 219, 219'
Piston-chamber combination. 105. The method of claim 104,
Wherein the container is sealably movable with respect to the chamber wall within the chamber,
Piston-chamber combination. 105. The method of claim 104 or 105,
The deformable material 103, 103 ', 124, 124', 136, 137, 173, 173 ', 174, 174', 205, 205 ', 206, 206', 215, 215 ', 219, 219' Fluids or fluid mixtures such as water, steam and / or gas, or foam-
Piston-chamber combination. 107. The method of claim 106,
The deformable material (124, 124 ', 136, 174, 174', 205, 205 ', 219, 219') is at least substantially incompressible,
Piston-chamber combination. 107. The method of claim 106 or 107,
The container includes an inflatable,
Piston-chamber combination. 105. The method of claim 104 or 105,
Wherein the combination further comprises a piston rod, the wall of the container comprising a flexible material vulcanized on the piston rod,
Piston-chamber combination. 108. The method of claim 109,
Wherein the wall of the vessel comprises at least one layer disposed closest to the piston rod and having a reinforcing material vulcanized thereon and one layer disposed on the layer comprising the reinforcing material and not comprising a vulcanized reinforcing material,
Piston-chamber combination. 112. The method of claim 110,
Stiffener reinforcements are placed parallel to the central axis of the piston,
Piston-chamber combination. 109. The method of claim 108 or 109,
Wherein the wall of the vessel comprises two stiffener layers, the stiffeners of the layers intersecting each other at a very small angle,
Piston-chamber combination. 6. A method according to any one of the preceding claims,
The shape of the elliptic piston maintains its shape at the second longitudinal position, but the length of the container-shaped piston is increased so as not to maintain its size when it is at the first longitudinal position,
Piston-chamber combination. 52. The method of claim 51,
A pressure regulator in communication with the pressure vessel and the third enclosure communicates with the pressure vessel,
motor. 52. The method of claim 51,
Wherein the third closed space of each cylinder is in communication with each other through a connection of two sub-crankshafts included in the crankshaft of the motor, and the second closed spaces of each cylinder are connected to the crankshaft (Fig. 19) communicating with each other outside the shaft,
motor. 116. The method of claim 115,
In the crankshaft configuration of the two piston-chamber assemblies, the connector rods are arranged 180 degrees from each other (Figure 19)
motor. 116. The method of claim 115 or 116,
And the second closed space is connected to the second closed space of the sub-crankshaft of the cylinder to be added through the connection of the sub-crankshafts of the existing two cylinders (Fig. 19 ),
motor. 53. The method of claim 52,
The second longitudinal position of the first cylinder being equal to the geometrical level of the first longitudinal position of the second cylinder and the two actuator pistons communicating with each other via the crankshaft, Crankshaft, one for each actuator piston, the connecting rods for the actuator pistons are arranged 180 DEG from each other (Fig. 17)
motor. 121. The method of claim 118,
Further comprising ESVT pumps for each cylinder such that through the communication of the enclosed space of one of the actuator pistons with the confined space of one of the actuator pistons the pumps are combined into one pump for the two cylinders, The closed spaces are contained in the crankshaft, and the closed spaces communicate with each other at connection points of the sub-crankshafts (Fig. 17)
motor. 120. The method of claim 119,
Further comprising a valve for opening and closing a connection between the ESVT pump and the second or third enclosed spaces when the respective connection has a check valve or a check valve function, And the tappet is in communication with the camshaft communicating with the main shaft of the auxiliary motor (Fig. 17)
motor. 119. The method of claim 118,
Further comprising more than two cylinders, each of the additional cylinders being communicated through an enclosed space of connected sub-crankshafts of existing sub-crankshafts (Figure 17)
motor. 53. The method of claim 52,
The first longitudinal position of the first cylinder being equal to the geometrical level of the first longitudinal position of the second cylinder and the two actuator pistons communicating with each other via the crankshaft, Crankshafts, one for each actuator piston, the connecting rods for the actuator pistons are arranged at 0 [deg.] From each other (Fig. 18)
motor. 124. The method of claim 122,
Further comprising ESVT pumps for each cylinder such that through the communication of the enclosed space of one of the actuator pistons with the confined space of one of the actuator pistons the pumps are combined into one pump for the two cylinders, The closed spaces are contained in the crankshaft, and the closed spaces communicate with each other at connection points of the sub-crankshafts (Fig. 18)
motor. 124. The method of claim 123,
Further comprising a valve for opening and closing a connection between the ESVT pump and the second or third enclosed spaces when the respective connection has a check valve or a check valve function, And the tappet is in communication with the camshaft communicating with the main shaft of the auxiliary motor (Fig. 18)
motor. 124. The method of claim 122,
The closed space (s) of each additional (coupled) cylinder (s) are separated by a filler connected to the existing sub-crankshafts, and the power of the added cylinders The stroke is performed simultaneously with the return stroke of the existing cylinders (Fig. 18)
motor. 53. The method of claim 52,
Further comprising two cylinders, wherein the connecting rods are disposed at 180 DEG from one another and the chambers have the same geometric position as the first and second longitudinal positions (FIG. 18)
motor. 126. The method of claim 115,
The piston-chamber assemblies for each enclosed space in the sub-crankshaft that change the pressure / velocity in the cylinder communicate with each other through the electrical pressure regulator of the bi-directional actuator, and the bi- Moving piston rod, communicating with external speeder,
motor. 127. The method of claim 115,
Wherein the piston rod of the pump for pressurizing the fluid in the piston is driven by a bi-directional actuator piston driven by a battery driven by an auxiliary power source,
motor. 128. The method of claim 115,
Wherein the piston rod of the pump for pressurizing the fluid in the piston is driven by a bi-directional actuator piston driven by a battery driven by an auxiliary power source,
motor. 129. The method of claim 115,
Wherein the piston rod of the pump for pressurizing the fluid in the piston is driven by a bi-directional actuator piston driven by a crankshaft driven by an auxiliary power source,
motor. 128. The method of claim 115,
Wherein the piston rod of the pump for pressurizing the fluid in the piston is driven by a bi-directional actuator piston driven by a camshaft driven by an auxiliary power source,
motor. 53. The method of claim 52,
Wherein the piston rod is sealably movable within the cylinder and the sealed space within the piston rod communicates with a pressure controller in communication with the remotely located speeder, the size of the sealed space Is controlled by a pump having a conical chamber on which an end slides over the cam profile, the cam profile being driven by an auxiliary electric motor for rotating the cam and rotating about the same main motor axis,
motor. 132. The apparatus of claim 132,
The actuator piston having a wall and a stiffener, the wall having an end fixed on the piston rod and a movable end mounted on the piston rod and sealingly slidable on the piston rod,
motor. (70) defined by an inner chamber wall (71, 73, 75), and at least a second longitudinal position between the first longitudinal position and the second longitudinal position of the chamber A piston-chamber combination comprising piston means (76, 76 ', 163)
Wherein the chamber has a cross-section of a different cross-sectional area at a first longitudinal position and a second longitudinal position of the chamber, and at least substantially continuously different cross-sectional areas at an intermediate longitudinal position between the first longitudinal position and the second longitudinal position, Wherein the cross-sectional area at the first longitudinal position is greater than the cross-sectional area at the second longitudinal position,
Wherein the piston means is adapted to pass through the intermediate lengthwise position of the chamber and, during relative movement of the piston means from a first longitudinal position to a second longitudinal position, The means are designed to be adjusted,
The piston means 1300 includes a plurality of reinforcing pins 1302, 1303 and 1304 rotatably coupled to a holder plate 1307 including a holder 1308,
The reinforcing pin is provided in an elastically deformable foam supported by the reinforcing pin for sealing against the inner wall (XXXX) of the chamber (70)
The reinforcing pin is rotatable about 0 to 40 degrees with respect to the longitudinal axis 1319 of the chamber 70,
The piston means (1300) comprises a resiliently flexible impermeable membrane (1305), the piston-chamber assembly comprising:
The reinforcing fin is made of metal,
The holder plate is made of metal and includes small closed round end holes 1329, 1330, 1331 arranged in more than one row 1326, 1327, 1328,
And the reinforcing pin is coupled to the holder plate by a magnetic force.
Piston-chamber combination. A piston-chamber assembly comprising a elongate chamber defined by an interior chamber wall and piston means in said chamber that is sealingly moveable relative to said chamber at least between a first longitudinal position and a second longitudinal position of said chamber ,
Wherein the chamber has a cross-section of a different cross-sectional area at a first longitudinal position and a second longitudinal position of the chamber, and at least substantially continuously different cross-sectional areas at an intermediate longitudinal position between the first longitudinal position and the second longitudinal position, Wherein the cross-sectional area at the first longitudinal position is greater than the cross-sectional area at the second longitudinal position,
Wherein the piston means is adapted to pass through the intermediate lengthwise position of the chamber and, during relative movement of the piston means from a first longitudinal position to a second longitudinal position, The means are designed to be adjusted,
The piston means comprising an elastically deformable container comprising a deformable material,
Wherein the deformable material is a fluid or fluid mixture, such as water, steam and / or gas, or foam, in a piston-chamber combination,
The wall of the vessel includes separate wall portions 2106, 2112, 2113, 2123, 2133, 2142, 2143, 2207, 22xx, 22xx ", 2244, 2244"; 2145, 2199, 2238, Characterized in that the portion has a greater circumference than the rest of the wall of the vessel and comprises an area of contact with the wall of the chamber.
Piston-chamber combination. (70) defined by an inner chamber wall (71, 73, 75), and at least a second longitudinal position between the first longitudinal position and the second longitudinal position of the chamber A piston-chamber combination comprising piston means (76, 76 ', 163)
Wherein the chamber has a cross-section of a different cross-sectional area at a first longitudinal position and a second longitudinal position of the chamber, and at least substantially continuously different cross-sectional areas at an intermediate longitudinal position between the first longitudinal position and the second longitudinal position, Wherein the cross-sectional area at the first longitudinal position is greater than the cross-sectional area at the second longitudinal position,
Wherein the piston means is adapted to pass through the intermediate lengthwise position of the chamber and, during relative movement of the piston means from a first longitudinal position to a second longitudinal position, The means are designed to be adjusted,
The piston means 1300 includes a plurality of reinforcing pins 1352, 1353 and 1354 rotatably coupled to a holder plate 1358 including a holder 1359,
The reinforcing pin is provided in a resiliently flexible foam supported by the reinforcing pin for sealing against the inner wall (XXXX) of the chamber (XXXX)
The reinforcing pin is rotatable about 0 to 40 degrees with respect to the longitudinal axis 1319 of the chamber 70,
The piston means (1300) comprises a resiliently flexible impermeable membrane (1305), the piston-chamber assembly comprising:
The reinforcing pin is made of plastic and has spherical ends 1355, 1356, 1357,
The holder plate includes small closed spherical spherical cavities (1360, 1361, 1362) arranged in more than one row (1326, 1327, 1328)
The spherical end being coupled to the spherical spherical cavity,
Characterized in that the holder plate further comprises openings (1363, 1364, 1365) for guiding the reinforcing pins.
Piston-chamber combination. 136. The method according to any one of claims 1 to 136,
Further comprising a circular chamber 4001,
The piston 4000 moves around the center point 3995 of the chamber and the connecting rod 4003 has a central axis 4008 and the axis 4002 has a central axis, 4003 coupled to the shaft 4002,
motor. 136. The method of claim 137,
The connecting rod 4003 is disposed perpendicularly to the axis 4002 and the center axis 4008 of the connecting rod 4003 and the center axis of the axis 4002 penetrate the center point 3995,
motor. The method of claim 137 or claim 138,
Further comprising an extension rod 4020,
The connection rod 4003 is connected to the piston 4000 through an extension rod 4020 and is connected to the end 3991 of the extension rod 4020 and the center axis 3996 of the chamber 4001, (1, 1 ') between the intersection points (3990) of the central axis (4008)
motor. The method of claim 137 or claim 138,
A pressure management system and a hub for mounting the connection rod on the shaft, the piston 4000 having a channel 4004 of the axis 4002 and a channel 4006 of the wall of the axis 4002 A channel 4006 of the hub 4009 and a channel 4005 of the connection rod 4003 and a space 4026 of the piston 4000. The channel 4025 of the hub 4009, ) Communicating with the pressure management system through a channel (4027) of the extension rod (4020)
motor. 143. The method according to any one of claims 137 to 140,
The hub 4009 includes a contra-weight 3994,
motor. 143. The method according to any one of claims 137 to 141,
The shaft 4002 is slidably mounted on the connecting rod 4003 by a hub 4009 and the hub includes teeth 4007 that fit into a groove 4007 '
motor. 143. The method of claim 142,
Each of the channels 4025, 4006, 4006, and 4008 of the extension rod 4020, the connection rod 4003, the wall of the hub 4009, the wall of the shaft 4002, The communication between the pressure management system and the interior 4026 of the piston 4000,
motor. 143. The method according to any one of claims 137 to 143,
The shaft 4032 is connected to the connection rod 4033 by a hub 4038 including a tooth 4007 fitting to a groove 4007 'of the shaft 4002, and the circular chamber 4001 And is connected to the shaft 4002 through a spoke 4034 mounted on the hub 4035. A bearing 4039 is disposed between the hub 4035 and the shaft 4002, And the channel 4044 of the wall of the axis 4032 and the channel 4046 of the connecting rod 4033 through the channel 4045 of the wall of the hub 4038. [ The bearing is disposed between the shaft 4032 having a channel 4043 constantly communicating with the channel 4034 of the shaft 4032 through the shaft 4032 (FIG. 91)
motor. 144. The method of claim 137,
The bearing 5100 is part of a hub 5101 that assembles a connecting rod 5102 (via a piston) to the shaft 5103 and a hub (not shown) that connects the spoke 5105 to the shaft 5103 5140 and the connecting rod 5102 has a channel 5109 and the shaft 5103 has a channel 5114 and the communication between the channels is blocked by the bearing 5100 91c and 91d)
motor. 145. The method of claim 144 or claim 145,
The axis 4002 includes an additional channel 4041 formed by a reduced diameter of a portion 4046 of the axis 4040 which is located near the channel 4042 of the wall of the portion 4046 Lt; / RTI &gt;
motor. 145. The method of claim 146,
The communication between the channel 4035 of the connecting rod 4003 and the channel 4034 of the shaft 4032 is constant,
motor. 147. The method of any one of claims 137 to 147,
Further comprising three circular chambers, the housing, the hub, the motor shaft and the gear box, in which the pistons move inwardly, the chambers 4092 being disposed parallel to one another and interconnected by the housing 4095, The motor shaft 4094 is assembled on the motor shaft 4094 by a hub 5005 and the motor shaft 4094 is directly connected to the shaft 5004 of the gear box 4093 including the drive shaft shaft 5000 And a channel 5002 inside the motor shaft 4094 communicates with the closed space 5003 of each piston 4091 and communicates with the pressure management system 5001,
motor. 147. The method of any one of claims 137 to 147,
Further comprising gears having three circular chambers in which the pistons move, a housing plate, a motor shaft and a variable pitch wheel and a belt, the chambers being connected to each other by the housing plate (5017) 5011 are connected to the motor shaft 5013 by a hub 5019 and a connecting rod 50xx and a pitch wheel 5014 is disposed on both sides of the motor 5010 and the variable pitch wheel 5014 Are connected to similar wheels 5015 by a belt 5021 mounted on a wheel axis 5016 of the vehicle, the variable pitch wheels 5014, 5015, 5014 ', 5015' are pitched high and low, The distance x between the wheel axes 5016 of the pitch wheels 5014, 5015, 5014 ', 5015' is constant,
motor. 147. The method of any one of claims 137 to 147,
(5023, 5023 ') is connected to each of the chambers (5021), and the chambers (5023, 5023') are connected to the respective chambers The central axis 5022 includes a bearing 5033 and an inner axis 5032 which is connected to the inner space 5032 of each piston 5025 through a hub 5034 and a channel 5039 of a connecting rod And a channel 5037 communicating with the central axis 5022 and communicating with a central axis 5022 of the piston 5025. The center axis 5022 includes a portion 5022 ' And the hub 5034 is mounted on the inner shaft 5032 and the center shaft 5022 is connected to the outer gear box 5024 and the outer gear box 5033. [ And each chamber 5021 includes a ring 5026 disposed furthest away from the central axis 5022,
motor. 155. The method according to any one of claims 1 to 150,
In particular, a motor is mounted on each of two parallel disposed wheels, the wheels are rotatable about a center, and the pressure for each of the motors 1970, 1971 The management system is respectively controlled by the rotation angles a and b through the signals 1981 and 1982 transmitted to the computer 1983 and the angle a is greater than the angle b, (1984, 1985) to the motor (1970, 1971)
motor.

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