JP2024045410A - Piston-chamber combination Vanderblom motor - Google Patents

Abstract

A piston and chamber combination for use in pumps and the like is provided. The piston-chamber combination comprises a chamber (186) bounded by an internal chamber wall, and an actuator piston within the chamber slidable relative to the chamber wall between a first longitudinal position (208) and a second longitudinal position (208') of the chamber. The chamber has a cross-sectional area and a cross-sectional area of different circumferential lengths that vary continuously between the first and second longitudinal positions, and the piston comprises an elastically deformable vessel, the piston having a production size of the vessel in a stress-free and undeformed state. This is accomplished by providing a means for allowing pressurization of the vessel by introducing a fluid into the vessel from a position outside the vessel, thereby expanding the vessel, and providing a wall of the piston providing a smooth surface at and near its contact area with the wall of the chamber, thereby moving the vessel from the second position of the chamber to the first longitudinal position. [Selected Figure] Figure 1-1

Description

The present invention relates to a piston-chamber combination Vanderblom motor.

a piston bounded by an internal chamber wall and engageable against the chamber wall between at least first and second longitudinal positions of the chamber wall; , wherein the first and second longitudinal positions of the chamber have cross-sectional areas of different cross-sectional areas and different circumferential lengths, and a longitudinal direction intermediate between the first and second longitudinal positions of the chamber; the positions have at least substantially continuously different cross-sectional areas and different circumferential lengths, the cross-sectional area of the first longitudinal position being greater than the cross-sectional area of the second longitudinal position; The actuator piston includes a container having an elastically deformable container wall for engagingly contacting the chamber wall, the container providing different cross-sectional areas and different circumferential lengths of the piston. a piston-chamber combination that is elastically deformable such that during relative movement of the piston between the first longitudinal position and the second longitudinal position through the intermediate longitudinal position of the chamber; In order to accommodate different cross-sectional areas and different circumferential lengths of the chamber, the actuator piston is configured such that the production size of the container is such that the circumferential length of the actuator piston is equal to the circumferential length of the chamber in the second longitudinal position. Manufactured to approximately equal stress-free and undeformed conditions.
(19627 Background of the invention)
The present invention deals with solutions for actuators that function alternatively and efficiently in relation to existing actuators, and also provides an important solution for actuators for motors, especially automotive motors, to combat climate change. Handle goals. Furthermore, the invention deals with solutions for efficient shock absorbers and pumps.

The present invention specifically deals with a solution to the problem of obtaining a motor that does not use the flammable technology of oil derivatives such as gasoline, diesel, and is able to compete with current motors based on said flammable technology. In addition, to meet the demand for reduced CO2 emissions, it does not require a new electrical grid as an energy source for the motor, as it competes with H2 and even air-based flammable motors.

Combustible motors based on oil derivatives are, after current technical standards, only an optimized version of a concept from about a century ago. This means that they cannot meet today's standard of living. namely, sources of pollution such as the precious and limited availability of petroleum, toxic gases such as CO, and emissions of gases such as CO2, which are important contributors to climate change. Additionally, since combustible motors tend to be heavy, the transportation weight ratio (weight to total transportation weight per person) for passenger cars is approximately 12 to 33 (limousine, 4-wheel drive) for small passenger cars. .

New combustible motors based on H2 or air lack a distribution network, like a gas station, that provides an energy source to supply gasoline, diesel, NLG gas. Even current motors that work on air require a "filling station" to provide the necessary highly compressed air in large and heavy cylinders. The lack of such a distribution network is because said motors on air are constructed in such a way that they can also work on combustible means, e.g. gasoline or diesel, which is thus sent back again to the otto motor, and should be avoided.

The establishment of new supplier networks for the use of the aforementioned combustible materials requires very high financial investments and poses difficulties due to the Catch-22 situation. Without a properly fine-masked network, these motors will not be distributed. This is because no one would buy such a motor because it is not commercially available, and no one would want to invest in a network before there is evidence that a market exists. In order to quickly introduce and widely disseminate pollution-free motors, it is necessary that these motors be independent from the network that supplies the energy source. The current development of home refueling stations for H2 is interesting but appears to be very difficult to handle as it is a very dangerous gas and should only be handled by directed personnel.

The object of the present invention is to provide a piston and chamber combination for use in pumps, actuators, shock absorbers, and in particular an actuator combination for use in motors.

In a first aspect, the invention relates to a piston and chamber combination. The combination includes means for introducing fluid from the location.
Pressurizing the container external to the piston expands the container and moves the container between a second longitudinal position and a first longitudinal position of the chamber.

A classical actuator piston is arranged in a linear cylinder, said piston comprising a piston rod. This piston is moving as a result of a pressure difference between both sides of said piston, said piston may be made of a non-elastic material and at least comprises a sealing, sealing the piston to the cylinder wall, in which the piston is relatively moving in said cylinder. The piston rod may be guided by bearings on one or both sides of the cylinder. The piston rod outside the cylinder may push or pull an external device. It may also engage a crankshaft, causing a rotation of the crankshaft axis, which may result in a movement of the vehicle, including said actuator and crankshaft, for example.

The actuator piston, when arranged in a linear cylinder, may be an expandable piston, for example a container piston according to claim 5 and claims 28 and 34 of EP 1 179 140 B1. If said expandable piston is internally pressurized, its walls are preferably capable of engaging or sealing, respectively, with the walls of the cylinder, as in the above-mentioned classic piston in said straight cylinder. , can act on its movement within said cylinder. To enable movement, valves on both sides of the piston, e.g. the walls of the chamber, are required, and fluid in the cylinder on either side of said piston with a constant pressure difference, preferably controlled by control means. be. Changing the magnitude of the pressure inside the last-mentioned container wall can only affect the ability of said piston wall to engage or seal to the chamber wall. Nevertheless, via the friction between the walls of the container and the walls of the chamber, said internal pressure can influence the speed of movement of the piston.

The actuator according to the invention is a piston-chamber combination with an expandable piston. The interior of the piston may preferably be fluid and/or foam under constant pressure, the walls of the piston include material and preferably reinforcement, and the piston is capable of changing shape. can. and/or size, and/or the piston may move within the chamber, preferably without requiring a fluid within the chamber, and/or requiring a pressure differential of said fluid or foam on either side of the piston within the chamber. Instead, the fluid in the chamber may of course be present as air at atmospheric pressure, for example for control purposes.

A further necessary parameter is that the chamber walls are not parallel to the central axis of the chamber, but rather the angle of the chamber walls in the direction of the intended movement of the piston has a positive value, so that the piston can expand in said direction. The expansion can preferably take place from the second longitudinal position of the piston (smallest circumferential dimension of the piston: unstressed production size) to the first longitudinal position of the piston (largest circumferential dimension of the piston: see EP 1 384 004 B1).

The motion of the piston may be initiated by forces towards the inner chamber wall of the reservoir piston that arise when the reservoir is expanding. The motion may therefore be initiated by reaction forces from the chamber wall to the reservoir wall. These forces are in reaction to the expansion of the reservoir wall, which may be the result of increasing the volume and/or pressure of fluid within the piston as a result of the introduction of more fluid through an enclosed space from a location outside the piston into the reservoir.

In the working prototype of the piston according to Fig. 7A-C (WO 2004/031583), Fig. 8D (WO 2004/031583) is a piston oscillating from a second longitudinal position to a first longitudinal position, in a chamber having, when no load is applied, a so-called constant maximum working force shape (WO 2008/025391-Fig. 6B), a velocity that fluctuates in excess of the pressure in the piston already by a few bars in relation to the atmospheric pressure that existed on both sides of the piston in the chamber, and a fluctuating positive angle of the inner chamber wall with the central axis of said chamber in the direction from the second longitudinal position to the first longitudinal position. The fluctuations in the piston velocity have been experienced and are explained below.

The contact between the vessel wall and the chamber wall can be engaging or sealing. As the prototype shows, it depends more or less on the load on the piston rod. When there is no load on the actuator, the contacts can be engaged without being sealed. When there is a load on the actuator, the driving force on the vessel is greater than when there is no load on the actuator, and there is enough force from the vessel wall to the chamber wall that they make contact.

The space between the walls is sealed. It is also possible to continuously engage and seal the contact with the walls of the chamber during movement of the piston.
Possible reasons why the piston is moving are as follows. The longitudinal component of the reaction force from the chamber wall to the vessel wall (directed toward the first longitudinal piston position) is the longitudinal component of the frictional force between the chamber wall and the piston wall (directed to the second longitudinal piston position). directed to the longitudinal piston position), the resulting total force is directed to the first longitudinal piston position, with the result that the piston moves from the second longitudinal position to the first longitudinal position. The end of the container closest to the second longitudinal piston position is preferably fixed to the piston rod by the cab (192), so that the piston rod moves as well. Self-propelled actuators are emerging, which can replace the piston in the chamber, which is moved by a pressure differential outside the piston. Preferably, the other end of the container is slidably movable on the piston rod by the cab (191), which is caused by movement of the cab (191) on the piston rod toward the cab (192). This means bringing the cabs (191) and (192) closer together. This is due to the selected reinforcement of the walls of the container, which is preferably one layer of reinforcing strings directed from the cab (191) to the cab (192), which layer (e.g. WO2004/031583, Figure 8D), optionally with a slight angle at which the central axis of the chamber and/or the at least two reinforcing layers intersect each other at a very small angle .

Due to the positive inclination of the walls relative to the central axis of the chamber in the direction of the first longitudinal piston position, and the fact that the contact surface of the piston and the wall of the chamber are located longitudinally, preferably below, optionally approximately below, the midpoint of the elastically deformable wall of the piston, the movement motors the expansion of the walls of the container. Thus, the initial contact area between the walls becomes larger and the frictional forces increase. The movement may slow down as the overall resulting force towards the initial piston position decreases.

At the same time that the wall of the container between the increased contact area and the movable cap is expanding, the movement causes the cap (191) of the movable end of the piston to move closer to the cap (192) fixed to the piston rod, which means that there is still an overpressure in the container (potentially requiring a sealed volume).

The movement from the second longitudinal piston position to the first longitudinal piston position is constant, and the rebar in the wall of the vessel expands in a similar manner than the circular one closest to the second longitudinal position. This means that the vessel wall rolls over the chamber wall, and the contact area moves towards the first longitudinal position, thereby increasing the reaction force component of the chamber wall towards the vessel wall. The resulting force component towards the first longitudinal piston position increases and becomes more rapidly than the friction component, and therefore the part of the vessel closest to the second longitudinal piston position moves with increasing speed towards the first longitudinal piston position, thereby taking with it the non-movable cap (192) and the piston rod (the piston moves from the second longitudinal piston position to the first longitudinal piston position) as well.

Overpressure is measured with respect to atmospheric pressure, which may preferably be under atmospheric pressure if the piston may be positioned in a sealed chamber, such that it can communicate with the surroundings of the combination. This is why the aforementioned may be required on both sides of the piston.

Instead of a sealed chamber space, the fluid in the chamber can be in communication with the sealed chamber space, so that the fluid in the chamber does not impede the movement of the piston. This is a concept that can be used in shock absorbers.

Whether a closed chamber space or a channel to the atmospheric environment is required depends on the ability of the piston to seal to the chamber wall. Since 100% sealing of the piston to the chamber wall is not required (engagement), leakage to the piston wall may also be due and present. Thus, the channels connecting the spaces of the chambers on each side of the container may be interconnected by channels provided by the piston.

The piston may include a closed space, for example a hollow piston rod. The inside of the piston may communicate with the sealed space. The volume of the closed space may be constant, variable, or adjustable. The closed space communicates with a pressure source.

In a second aspect, the invention relates to a piston-chamber combination further comprising means for removing fluid in the piston-chamber combination from said reservoir through said enclosed space to a position outside the piston, thereby allowing said reservoir to be retracted. The movement of said piston from a first longitudinal position to a second longitudinal position during the return part of the stroke can be achieved by at least three possible methods.

The conventional method is that the piston sealingly engages with the walls of the chamber. However, the movement may cost energy, since the excess fluid in the receptacle-type piston will contract, thereby reducing the internal volume, and be transported towards the closed space, whose internal pressure may rise. To save energy, the piston may engage but not seal with the walls of the chamber. This reduces the frictional forces between the piston and the chamber walls. The last method can be done by sucking the fluid out of the receptacle, by lowering the internal pressure of the receptacle during the portion of the stroke. This can be done by a control means, controlling the pressure in the closed space.

In a third aspect, the invention relates to a combination of a piston and a chamber. The piston is movable relative to the chamber wall from at least a first to a second longitudinal position of the chamber. It is possible to move the piston from the first longitudinal position to the second longitudinal position without engaging the chamber wall. This can be done by reducing the pressure in the piston to a minimum level, for example by ensuring that the walls of the piston are not stressed and that its periphery is of its production size at the pressure at which the piston is produced (e.g. atmospheric pressure), so that the piston can reach the second longitudinal position without jamming.

In a fourth and fifth aspect, the invention relates to a piston and chamber combination. The piston includes a piston rod that includes the sealed space. The piston is provided with engagement means outside the chamber. The suspension of the piston rod, for example according to the bearing type shown in WO2008/025391, for guiding the piston during said part of the stroke without guidance of the piston itself, if the piston does not engage with the walls of the chamber. It may be very special.

A piston rod may extend from the piston in one longitudinal direction and is guided by a bearing at the end of the chamber. This means that the piston rod may contain an enclosed space and may also be arranged outside the engagement means, eg the chamber. The engagement means can be pushed or pulled when the piston is moving from the second longitudinal position to the first longitudinal position. Otherwise, the engagement means cannot be pushed or pulled. A force external to the piston drives the piston from the first longitudinal position to the second longitudinal position. If the piston constitutes a piston rod, the force on the piston rod may be driving the piston if the piston is not moving sealingly from the first longitudinal position to the second longitudinal position. be. This may be achieved by said engagement means.

However, it is also possible for the piston to comprise two longitudinally extending piston rods, one piston rod usually being a continuation of the other piston rod. One or both piston rods may be arranged outside the engagement means, eg the chamber. If both piston rod ends extend outside the chamber, one bearing of the piston rod may be rigidly fixed to the chamber and the other bearing may float relative to the chamber. The engagement means can be pulled and pushed simultaneously when the piston is moving from the second longitudinal position to the first longitudinal position. Another method is the return stroke. The engagement means will not be able to be pushed or pulled. A force external to the piston drives the piston from the first longitudinal position to the second longitudinal position. If the piston constitutes a piston rod, the force on the piston rod drives the piston when the piston is not moved sealingly from the first longitudinal position to the second longitudinal position relative to the chamber. There is a possibility that there are. This may be achieved by said engagement means.

In a sixth and seventh aspect, the invention relates to a piston and chamber combination, wherein the piston rod is connected to a crankshaft. The crank is adapted to translate the movement of the piston. A second longitudinal position and a first longitudinal position of the chamber enter rotation of the crank. The crank is converting the rotation into movement of the piston from a first longitudinal position of the piston to a second longitudinal position of the piston.

The engagement means may be a crankshaft, which is connected to the piston by said piston rod. In order to be able to at least initiate the movement of the piston from the first longitudinal position of the chamber to the second longitudinal position, the crankshaft should rotate before said movement is initiated by said piston, so that the impulse of the relative weight of said crankshaft generated by the movement of the piston from the second longitudinal position to the first longitudinal position is transmitted to the piston.

Another option is that the movement of the piston between the first and second longitudinal positions may be effected by movement of the crankshaft initiated by another piston-chamber combination, for example where the pistons move simultaneously from the second position of the chamber to the first position (at least two cylinders working together on the same crankshaft).

The initial movement of the piston is initiated, for example, by an electric motor (
A type of starter motor may also be used.

In seventh and eighth aspects, the invention relates to a piston and chamber combination, wherein the piston rod is connected to a crankshaft. The crankshaft includes a second sealed space. The second enclosed space is in communication with a power source. The crankshaft may be hollow and may include a second enclosed space. This means that the crankshaft axle and its contraweight are hollow so that they form a groove together from the canister-shaped piston towards the end of the crankshaft axle. In an O-ring seal, this channel may communicate with a pressure source. Furthermore, the bearing of the crankshaft may be disposed within the crankshaft and communicated with an external power source.

In a ninth aspect, the invention relates to a combination of a piston and a chamber; - said second closed space is in communication with a first closed space in the piston rod during the time that the piston is moving from the first longitudinal position to the second longitudinal position of the chamber; - during the part of the stroke from the first longitudinal position to the second longitudinal position, the piston may be decompressed to a certain pressure level created by connecting the first closed space in the piston to a second closed space in the crankshaft for the required time during which the piston is moving from the first longitudinal position to the second longitudinal position; - the pressure level created by the piston may not be atmospheric pressure, but any pressure level; - the higher the pressure level, the less energy is lost when the first and second closed spaces are connected to each other;

In a tenth aspect, the invention relates to a piston and chamber combination. The crankshaft comprises a third enclosed space, which space is connected to the first portion of the piston rod during the time the piston is moving from the second longitudinal position to the first longitudinal position of the chamber. Communicates with a closed space.

This third closed space has the function of repressurizing the piston when the piston moves toward the first longitudinal position of the chamber toward the final second longitudinal position of the chamber. The pressurization is performed by repressurizing the third closed space, which is overpressurized relative to the first closed space, to the first closed space.
This is done by connecting the closed space to the piston so that it can be pressurized as soon as possible after the piston changes direction.

In an eleventh aspect, the invention relates to a piston and chamber combination. The third enclosed space is in communication with the second enclosed space during the period when the piston is moving from the second longitudinal position to the first longitudinal position of the chamber.
Shock absorbers of the following configurations, combined according to all the aforementioned aspects,
means for engaging a piston from a position external to said chamber, said engaging means comprising an external position in which said piston is in a first longitudinal position of said chamber; and an inner position in a longitudinal position. The shock absorber may further comprise an enclosed space that can communicate with the container. The enclosed space may have a variable volume or a constant volume. Volume is adjustable.

The shock absorber can include a container and an enclosed space that can form an at least substantially enclosed cavity containing a fluid, the fluid being transferred from a first longitudinal position of the chamber to a second longitudinal position of the chamber. It can be compressed when moving into longitudinal position.

1. A pump for pumping a fluid, the pump comprising: means for engaging a second piston in a second chamber from a position outside the chamber; a fluid inlet connected to the second chamber and comprising a valve means; and a fluid outlet connected to the second chamber.

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

The engagement means 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 piston and chamber combination technique can be used in motors, especially automotive motors, and especially self-propelled actuators.
The piston may also move within the chamber, which may be cylindrical or conical (not shown), relative to the tapered wall.
The chamber in which the (actuator) piston is arranged may be of a type in which the chamber comprises an internally convex wall of longitudinal cross-section close to the first longitudinal position, said chambers being divided upwardly from each other by a common boundary. the distance between two common boundaries defines the height of the walls of said longitudinal section, said height decreasing by an increase in the internal overpressure rate of said piston, or In the direction up to two longitudinal positions, the transverse length of said common boundary may be determined by the maximum labor force selected for said common boundary, and may be determined by said maximum labor force. good.

Additionally, the chamber may include a cross-sectional boundary wall parallel to a central axis of the chamber.
And, the piston-chamber combination may include a transition between the convex wall and the parallel wall, where the transition may include a concave wall that may be located near at least a second longitudinal position.

The piston-chamber combination may include a concave wall, the concave wall comprising:
It can be placed on a convex wall from at least one side.
19627 Overview of the invention - Feasibility study Please see Figure 10 (B) and Figure 11 (B) for the feasibility study of the green motor. This means that an expandable actuator piston in a chamber of successively different cross-sectional areas is moved by the internal pressure from the smallest cross-sectional area to the largest cross-sectional area, thereby reducing the internal pressure, while during the return stroke, The fluid in the actuator piston is further depressurized and the fluid is recompressed by a cascade pumping system using an energy efficient piston-chamber combination according to WO2000/070227, at least one step of which A system in which the power of the motor is generated by a new propulsion system energized by a power source, for example the sun, preferably any other sustainable power source, or optionally a non-sustainable power source. Furthermore, a more efficient and reliable solution is shown in the figure. 11G and 13F. The system complies with the aforementioned specifications.
Conversion Power Supply for a "Green" Motor Based on the Principle of Figure 11A The system solution according to the invention provides that the "green" motor itself may be based on structural elements comparable to those currently used in combustible engines. , new structural elements need to function much more efficiently than those of current combustible motors, and the energy used can preferably be obtained from "green" energy sources. Preferably a pressurized fluid, preferably at low pressure (e.g. about 10 bar), is applied once, for example by solar, H2 refillable storage tank + fuel cell, or optionally by H2 refillable storage tank + fuel cell. , optionally filled and recompressed throughout the motor being manufactured, preferably during operation of said motor, refilled when the motor is not being manufactured, and preferably unfilled when the motor is being manufactured. , preferably continuously when the motor is filled. The motor is recharged when it is not running and/or possibly from the system itself, which means that the energy required is because it may be less than the total available energy that can be operated from the power source of
WO2000/070227 states that in the second longitudinal piston position, for example 10 bar of 8 Bar (in the second longitudinal position) in a tube of φ17 mm (from φ60 mm in the first longitudinal position), the minimum of the chamber Discloses a piston-chamber coupling technology that can save a considerable amount of energy, such as up to 65% of the energy of the pump in the second longitudinal position, if the cross-sectional area is placed in the position where the highest pressure occurs are doing. On the contrary, equal efficiency is obtained by using the technique with actuators instead of pumps. WO2004/031583 is
A disturbance within said chamber may be in a second longitudinal position if the unstressed production size of the piston has a circumference that is approximately the size of the circumference of that portion of said chamber that has the smallest cross-sectional area. Discloses expandable piston types (e.g., ellipsoid x sphere: small sphere x large sphere) that are not expandable. This piston type exhibits special characteristics for use as an actuator piston in the chamber, these characteristics being that the actuator can be moved from a pressure source outside the chamber by the piston in the second longitudinal position. It is self-propelled and in the working prototype it telescopes at 260 N in a chamber designed to have a constant maximum acting force of 260 N when there is no pressure difference between the two sides of the piston in the chamber. (WO2008/025391, WO2009/083274). This phenomenon can be used in this "green" motor, thereby exchanging motion based on the energy obtained from combustible technology, but still using the crankshaft. The energy used by the expansion is approximately 5 barz (eg 10 bar to 5 bar overpressure due to the increase in the volume of the piston), for example from an ellipsoid to a sphere to a constant volume of the closed space (WO2009/083274). Because on the return stroke the actuator piston needs to be unstressed in the second longitudinal piston position with its production size, for example with an internal overpressure of 0 bar. , this pressure drop must be re-obtained within the system. The enclosed space of the piston may be arranged in another enclosed space, for example in the crankshaft, for example when the pressure is increased again from 5 bar to 10 bar through a two-stage pumping process, the initial longitudinal piston position The 5 bar excess pressure in can be reused. This can be done efficiently by using another aspect of the piston-chamber coupling technique disclosed in WO2000/070227, resulting in even 65% in the recompression process.

For example, by using a piston according to claim 1 of EP1179140B1 or according to figures 5A-5H of WO2000/065235, energy can be saved, further developments of which are additionally claimed in the present invention. These 65% energy reductions can be achieved by, for example, connecting the pump crankshaft to the main crankshaft of the actuator piston, resulting in additional energy savings. The total savings is therefore 76.7% (65 + 1/3 x 35%). 23.3% of the energy is therefore obtained from another pump, for example the same as the one mentioned above, but now receiving its energy from, for example, a solar cell (which should not be larger than a solar cell built into the roof of a typical car, or into the paint of a car), or a fuel cell, or an electric motor which receives its electricity from said battery, optionally charged by a preferably alternator, and which can receive its rotation from the shaft of its own system or from the shaft of a small H2 combustible engine.

The energy required to realize its pumping function is 35% of 8.2% of 23.3%. This motor generates neither heat nor noise, but the weight of this motor can be substantially (for example, 60%) less than the weight of current combustible motors. Meanwhile, the additional control devices required by combustible motors, such as cooling water temperature, oil temperature, exhaust system, etc., are hardly required. Also, the gas tank with an aluminum body of the future vehicle may be half the weight of the current vehicle. For example, the VW Golf Mark II weighing 836 kg is designed and manufactured according to the present invention, but weighs about 425 kg. Only the driver TWR: 6,3!
The remaining problem is operating for long periods of time in the dark at night when only the solar cells can be used to recharge the battery, but the light from lamps on lamp posts on city streets may provide enough light for the solar energy cells.

Also, the speed of such "green" motors may be lower than that of current combustible motors, so a gearbox may be required.
19627 19618 Feasibility Study (revised)
Feasibility studies have not previously quantitatively incorporated the lack of heat generated by the motors of the present invention compared to Otto motor types.

It is even more interesting and compelling than the motor type of the present invention if heat losses can be incorporated. Heat losses can give current Otto motors 25% efficiency. In the first example, the motor type of the invention reduces the energy used to pressurize the fluid from 5 bar to 10 bar (10 bar was already present in the pressure storage vessel when the motor was manufactured). It is possible to assume that the motor type described above does not generate any heat (isothermal). The overall efficiency of the motor type according to the invention is less than 10%, i.e. 8,75% with a self-propelled actuator piston, which is unprecedented (David JC Mackay, Sustainable Energy - Without Hot Air - 2009) . If the regenerative pressure pump shown in the present invention again uses the piston-chamber combination of the present invention, another 65% of energy can be saved. Therefore, if we ignore that the heat is being generated by the pump, this is a total energy usage of 8.75% x 0.875 = 7.6%. However, if part of the energy used for pumping is not from another energy source (e.g. solar energy (photovoltaic) and/or a battery charged by a fuel cell (e.g. H2)) from a regenerative braking device connected to a flywheel or generator, the total amount of energy used is 10%
It is possible to end up with less than

As previously concluded, the motor type configurations according to Figures 11G, 15C or 15D and Figures 13F, G and 14D are the most efficient (simple construction, nearly isothermal thermodynamics) and also the most reliable. 13F, G and 13HD do not use crank-generated rotation, and the configuration of FIG. 13F will be used for quantitative evaluation of automotive motors.

In this invention, a current VW Golf Mark II model RF, 1600cc, weight 836kg, 53kW/71 pk petrol motor with 4 cylinders each φ81mm and 9 Bar pressure, and 77mm stroke is used as the benchmark for this invention. This gives a maximum force of 1159 N per cylinder, about 116 kg per cylinder. If all combustion parts are taken out of the body and aluminum is used instead of steel, a weight reduction of about 50% is assumed. Thus, the required weight per cylinder to drive the aluminum body is 58 kg, allowing the vehicle to drive up to 4 passengers and luggage.

The chambers of the pump shown in WO2008/025391 have diameters of φ58mm to φ17mm respectively, with a maximum force of 260N (26kg) and a total stroke of approximately 400mm from 2 to 10 Bar. Using an expandable elliptical piston within the chamber, the actuator has worked very well. Thus, two of these chambers are currently used as part of the actuator.
This is equivalent to removing one cylinder of the VW Golf Mark II petrol motor, and all the parts related to combustion, which are currently made from aluminium.

The motor of the invention changes the pressure in the enclosed space of the actuator piston from x bar (stroke: 2nd→1st longitudinal position) to approximately 0 bar (stroke: 1st→2nd longitudinal position). "x"
The value of can be chosen as small as possible to limit energy usage. By using this special chamber type, the magnitude of the working force does not depend on the pressure value, so by using a pressure window the pressure can be reduced to 3,5 bar at the highest level and about 0,5 bar at the lowest level. can be restricted.

This starting point is carried over to the configuration of the pressure in the spherical piston placed in the rotating chamber of Fig. 13F, but with 31/2 bar in said particular chamber for part of the stroke (216,2 mm out of 400 mm). The chamber may be of simpler shape, as shown in Figure 13F. The force per actuator piston is max. 260N.

This change in the volume of the sphere can be quite large as follows.
V2= 4/3×3,14×12,553(φ25.1mm; P2=0,35 N/mm2)=8280mm3～V1=4/3×3,14×23,453(φ46.9mm; P1=0,05 N /mm2)=54015mm3-, ΔV is 6,5 and ΔP=7. The angle of the wall with respect to the central axis of the chamber is good: L1=302,78-86,57=216,21, Δr=10,9: angle=2,9°.

The energy used for the "virtual" compression of the volume of said actuator piston at a first longitudinal position (index 1) into the volume of one cylinder at a second longitudinal position (index 2) is For a complete stroke L1:

Wisothermal = -P1V1ln(P2/P1) = 0.35 × 54015 × 7 = 0.35 × 54015 × 2,302585 × log 7 = 36788 Nmm/channel/piston/speed = 36,8 J/channel/piston/speed Invention The motor according to the above has a stroke rate not as fast as the gasoline motor (900 rv/m), but this is because the actuator piston made of reinforced rubber is assumed to expand and contract slowly. If the number of revolutions per minute is 60, it will rotate at 1 revolution per second (15 times slower than a flammable motor). W= 36,8J/channel/piston/s. There is a 2x4 "equivalent" chamber (cylinder) and the power is 294,3 J/s/piston, or more than 0,295 kW/piston. If 5 pistons are used, one for each of the 5 subchambers (Figure 13F) in the 360° channel, the generated power will be 5
×0,295kW = 1,47kW.

Checking the assumption of one revolution per second: with a 53 kW combustible gasoline motor, as stated earlier in this study, a saving of 92.4% is possible, while a saving of 7.6% would leave only 4,03 kW available.
If the number of rotations per second is approximately (rounded up or down), it is considered to be 3 rotations per second.

Thus, a motor with 2 x 4 "corresponding" chambers, each with 5 pistons in 5 subchambers, rotating at 3 revolutions per second (= 180 revolutions per minute) produces approximately 3 x 1,47 = 10 ...
4.4 kW - this might be enough to power a VW Golf Mark II with an aluminum body.
References (David JC Mackay, Sustainable Energy - Without Heat - p.127, Figure)
20.20/20.21) A small electric car has appeared that runs on about 4.8kW of power. This comes from 8x 6V batteries and can travel 77km on a single battery charge with a charging time of a few hours. This may be an option if the energy comes from batteries that cannot be charged while the vehicle is in motion, but is not the preferred embodiment.

How much energy is required to pressurize and depressurize an actuator piston, and can this be done while the car is driving?
We need to force a pressure change on the actuator piston of the motor. We use the principle shown in Figures 11F and 13F.

Energy is obtained from the kinetic energy from a rotating chamber, for example a piston of a classical piston-chamber combination, which is moved by a camshaft in communication with the main motor shaft of the motor. Using the data used to calculate the motor power, the change in pressure of the expandable spherical piston can be achieved by changing the volume of the enclosed space of the actuator piston by changing the "down" volume of the classical piston.

The volume change per stroke required by the actuator piston is achieved by the internal pressure change of said actuator piston from the second longitudinal position to the first longitudinal position, and therefore from a small sphere (φ25,1 mm) with a medium internal pressure (3,5 bar) to a large sphere (φ46,9 mm) with a low pressure (0,5 bar). The force is 260 N/stroke/piston, and regardless of the internal force, with 8 chambers made up of 5 pistons, the generated power is 4,4 kW at 3 revolutions/second.

The energy required to come from a first longitudinal position to a second longitudinal position is as follows (Figures 14A and 14B):
1. Increase the volume by changing the spherical shape of the actuator piston (φ46,9 mm; 0,5 bar) to the production shape (φ25,1 mm; 0 bar (overpressure)) and contracting the actuator piston into a closed measurement space. - This does not consume energy if the frictional forces between the pump piston and the walls of the confined space are small enough.
2. By reducing the volume of the enclosed space where the pump piston is close to the actuator piston, the energy required to inflate the sphere (φ25,1 mm, 0 bar) to (φ25,1 mm, 3,5 bar) is: It is as follows.
Wisothermal = -P1 V1ln(P2/P1)= -l (check this) × 4/3 × 3,14 × 12,553 × ln 4,5*/1 = -1 × 8280 × 2,302585 × log 4, 5 = 12454 Nmm/channel/piston/speed, per chamber for 2×4 chambers 5= 12,5 x 8 x 5 x 3 Js= 1,5 kW.
(*If P1 = 1 bar absolute, P2 absolute is 4.5 bar.
In this way, the generated Brut power is 4,4kW, and the power required to drive the motor is at least 1,5kW, so in addition to other final losses, about 2kW is required. be.

If a pump conforming to the above is present in the vehicle to access the motor, the current compressor has the following specifications: 220V, 170 1/min, 2,2kW, 8 Bar, pressure reservoir 100 1. We need a power source at a lower pressure so that this improved compressor charges the pressure reservoir a little faster.

For 8 Bar P = 2200 W, so for 31/2bar the same recompression time should be used as for 8 Bar. 3/8 x 2200 = 825 W only. Even if the battery is a 24V battery, the current will be 825/24 = 34,4A. This is very large for a battery, so there are many batteries available in the motor block diagram. 11A, B, G and fig. 12A, 13A
, pumps with reference numbers 826/831 must be electric. Recharging these batteries is only possible with an external power source, so the car should be disabled for many hours. That is, the capacitor solution (Figure 15E) is still in the research stage. This is not the preferred embodiment, but is an option.

It would be better to avoid the conversion of power and use the motor configuration of FIG. 15C, where the pump 826/831 is in communication with the axle of a combustible motor, for example using H2, preferably produced by electrolysis and optionally by a fuel cell. The aforementioned process is powered by electricity from a battery charged by an alternator in communication with said axle.

825 W needs to be generated by the combustible motor. This is 24cc / 66cc (VW Golf Mark II is 53kW, 1600cc, φ90mm, 4 cylinders → 825 W is about 24cc, 90mm 1 cylinder,
Or three times faster, about 2,2 kW could be about 66 cc, 90 mm 1 cylinder) classical motor, which can be compared to the large prime movers currently in use. A few months ago we saw mopeds on TV that electrolyze water, store it in a tank (originally for gasoline) and use the resulting H2 for the combustion process, but this is possible. Since a car is an external motor of this size, the extra combustibles that were previously removed from a VW Golf Mark II are now, unfortunately, in need of a replacement of the motor. There is no pollution or CO2 emissions, the noise could be improved by appropriate noise reduction measures, and the weight is 1/6 of the car and 15 1 water = 15 kg tank (= about 35 kg)
It is assumed that:
END Additions to the feasibility study descriptions in 19627, 19611 and 19618: A further development is that an expandable piston moves in a specially designed chamber so that the force generated by the piston is maximized with minimum expansion (=pressure drop), and that the interrupted movement of said piston, i.e. the "hesitation behavior" (see p.xx), can be compensated for by a modified internal geometry of said chamber.

The first-principles motor control of FIG. 1A is also novel for one actuator piston-chamber combination per crankshaft as follows.
It is assumed that the pressure storage vessel is pressurized only once by an external pressure source and could therefore have been pressurized during the production of the motor. The actuator piston can be started by an electric starting motor using a battery charged by a solar cell and/or by a classic dynamo rotated by the main shaft of the motor. The starting motor first rotates the crankshaft so that the actuator piston is internally pressurized. The pressurization of the actuator piston then takes over the initiative of the movement of the actuator piston and, as a result, the initiation of rotation of the crankshaft. The starting motor can then be disconnected from the crankshaft.

The motor can also be started by opening the pressure reservoir 814 so that fluid 822 pressurizes the actuator piston internally, which initiates the movement of the piston. See FIG. 1B.

Speeding up the motor, i.e. speeding up the rotation of the crankshaft, can be achieved by increasing the pressure in the actuator piston by opening a so-called pressure reducing valve in line [829] between the pressure vessel and the actuator piston. Slowing down the rotation of the crankshaft can be achieved by reducing the pressure in the actuator piston by closing the opening of the pressure reducing valve.

To give the motor more power (torque on the main shaft), this can be done by increasing the pressure to the existing configuration of actuator piston-chamber combinations, or there can be multiple actuator piston-chamber combinations per axle. Stopping the motor can be done by completely closing the pressure reducing valve in the (lead) line [829]. The pressure reducing valve may be connected to the speeder.

A more detailed pressure management of the actuator piston can be configured as follows: both the wall of the crank of the crankshaft and the end of the piston rod may be holes communicating with the second and third closed spaces and closed spaces respectively. At a certain point,
These holes may communicate with each other, such that the actuator piston sealed space communicates with the second or third sealed space in the crankshaft and communicates with the second sealed space. In this case, the piston may be pressurized through its sealed space and move from the second longitudinal position to the first longitudinal position in the chamber. While communicating with the third sealed space, a contraction of the piston may occur when the piston is moving from the first longitudinal position to the second longitudinal position. The main piston pump (818) initiates a pressure drop in the third sealed space of the crankshaft and a pressure drop in the sealed space of the piston rod due to the mutually relative default positions of the pump crankshaft and the actuator piston crankshaft, which may be assembled on the same axis, respectively.

More specifically, the actuator piston pressure management works as follows.
At a final second longitudinal position of the piston, a hole can be drilled.
Inputs Multiple actuator piston-chamber combinations in the motor may be on the same shaft. However, this concept may not be conducive to meeting the above specifications. As with current combustion motors, multiple piston-chamber combinations per shaft will allow the motor to run smoother. And, of course, the torque on the shaft will be increased.

As each CRANKSHAFT is organized, how do the actuator piston-chamber combinations work and how do they relate to each other?
The crankshaft itself is an inefficient way to generate rotary motion, and furthermore, the stroke length of this type of piston-chamber combination can be greater than that of, for example, a current-burning motor, i.e., the r(revolutions)p(er)m(inute) of said crankshaft can be substantially lower than that of a current-burning motor. Gears are required, and the gear ratio may be different from that of current-burning motors. The gearbox can reduce the efficiency, for example, by 25%, and said efficiency can be improved (for example, by 50%) by using low-friction bearings, such as hydrodynamic bearings. A clutch may be required, since the motor runs all the time. Thus, 33.2% of the energy required for the motor of the car should come from, for example, green energy, e.g., solar energy from solar cells on the roof/hood/full-body paint of the car, which may be excessive. Of course, it is also possible to add special batteries in case of charging with wind or solar energy. This increases the weight of the vehicle and increases the WTR ratio. In such cases, a power distribution structure is partially required. Therefore, this type of motor may not fully meet the above specifications, for example when targeted as a "green" vehicle motor.

Therefore, to meet specifications, crankshafts can be avoided as well as gears. A rotating power source for a "green" motor based on the principle of Figure 2(a). Therefore, it is possible that this piston rotates instead of translating. This new type of motor may be a type of "green" Wankel motor.
Al
At least for propulsion systems, an even better use of energy is obtained with a motor without a crankshaft, using the same principles as described above. In addition to the above, this reduced energy usage reduces the distance from the first rotational position to the second rotational position of the piston within the chamber, so that the motor can move the shaft almost continuously. can be specifically obtained in a chamber around a circular centerline that can be arranged concentrically around the main axis of the motor by shortening the radial axis to approximately the radius of the piston.
Al
The piston can act as a self-propelled actuator and is curved circularly in the longitudinal direction, forming a conical chamber that can fill 360° or part thereof. There may be at least one piston functioning within said chamber. The motor can include one of a plurality of actuator piston-chamber combinations, and these combinations can use the same axis. The center of the circular movement of the actuator piston and/or the chamber can be provided with an axle that is connected to the vehicle or to other vehicle-propelling structural elements, such as wheels.

There are two ways to configure such a motor. One is to move the central axis of the actuator piston rod in the plane in which the central axis of the chamber lies. Another possibility is that the central axis of the actuator piston rod can be placed perpendicular to the plane in which the central axis of the chamber lies. In both cases, it is possible that either the actuator piston moves, or the chamber moves, or both.

Actuator pistons such as those used in elongated conical chambers, i.e. ellipsoids to spheres, and circularly bent pistons (e.g. WO2000/070227 - Figures 9A, B, C) in circularly bent chambers. It seems unlikely that the piston rod bearing of the actuator piston is missing because the chamber is circularly bent in its longitudinal direction.

Alternatively, actuator pistons of the (smaller) sphere to (larger) sphere and vice versa type may be used (e.g. WO2002/077457 Figures 6A-H, 9A-C), which The symmetrical shape allows the construction of the piston rod bearing to be less complex. For example, a piston rod may be arranged via the actuator piston perpendicularly to a plane in which a central axis of the circularly shaped chamber lies.

The actuator piston may move within the chamber due to the fact that the chamber is the same shape as the linear chamber used when using a transitional movement piston, but is now circular. .

However, the size of the portion of the wall of the piston perpendicular to the central axis of the chamber behind the transition central axis of the piston, and the line from the center of the piston to where the piston engages (or seals) with the chamber is substantially smaller than that of an ellipsoid (spherical piston) translating on the central axis of an oblong chamber. This is why the assumed power that each actuator piston (sphere-sphere) has may be smaller than an ellipsoid+sphere actuator piston. This requires motors where more than one actuator piston per chamber is used. Similar problems need to be added because the actuator pistons are moving in a staggered manner (see below) and multiple pistons in the same 360° chamber may create a smooth motion. Also, when the actuator pistons are fully expanded, a very short moment occurs where the pressure in the actuator piston drops, which may give a "moment of hesitation" in the motion. This allows the actuator pistons to be placed at different positions on the central axis of the chamber in order for one actuator piston to overcome the "hesitation" in the motion of the other actuator piston. As an example, if a 360° chamber is divided upwardly by four identical sub-chambers, the number of actuator pistons may be five, equally divided across 360°.

The main advantage of such rotary motors is that the length of the return stroke of the actuator piston from the first circular position to the second circular position is substantially reduced compared to the crankshaft option, and the circular Since the first position and the circular second position are in direct succession to each other in the direction of rotation, it may be at least the size of the maximum radius of the piston in the first circular position.

Therefore, the pressure drop and immediate pressure rise in the actuator piston needs to be managed.
There are two basic ways to vary the internal pressure of the actuator pistons. One option is that each of the actuator pistons may be connected by a channel to a valve that can increase or decrease the pressure in said actuator piston. Said valves can be steered by a computer so that the pressure in each actuator piston is optimal for its position in said chamber. Furthermore, said computer can control the pressure from a pressure vessel acting as a pressure source so that the distribution of the available pressure in each actuator piston optimizes the use of the available fluid pressure of said actuator pistons. A second option is for example by a very short change in the volume of a closed space. This change can be made for example by a movable piston hermetically connected to the wall of an elongated chamber. Said chamber can be of the kind with a different cross section in the transition direction. Due to the speed of movement, this chamber can be of the kind with a constant circumference so that the piston only bends during the movement. But of course a chamber with a transition circumference of different size can also be an option. The piston moving in said chamber can have a piston rod in communication with a can disc, which can be connected to an axis on which a motor is attached. The end of the piston rod can be provided with a wheel rolling on said can disc. This motor type therefore does not consume any fluid, only the energy content (pressure) of said fluid.

The 360° chamber can revolve around an axis, the central axis of which can cross the center of the chamber. The chamber may be part of a wheel, and the outer part of the wheel may have a notch in which a drive belt can drive an auxiliary device, such as an electrical generator.

Obviously, a type of motor that does not move the two options of a motor with rotating chambers and pistons that can rotate is a less complicated solution. Also, since there are five times more pistons per chamber of the same dimensions, the torque generated is, for example, five times better than in the solution.

The most reliable system is a fixed piston in a rotating chamber. One advantage is that
The advantage of this motor is that it can be equipped with several pistons, for example five pistons, each of which can be located in a different rotational position, allowing the motor to rotate smoothly, since the transition of the piston from the first rotational position to the second rotational position is powered by, for example, four other pistons. Also, the "hesitation behavior" of the piston during the movement from the second rotational position to the first rotational position (see below) may also be supported by, for example, four other pistons, and no "hesitation" is observed. A gearbox is unnecessary, since the pressure velocity of the fluid inside the piston determines the speed of the main shaft, and this required pressure window can be easily obtained by the structure of this motor, and this pressure can be easily determined by the speeder. Thus, the gearbox may be superfluous, which adds a further weight reduction of about 50 kg. The conversion of the VW Golf Mark II was reduced to about 350 kg in addition to this. The TWR is now about 5,6.

Controlling a rotary motor can be done in a similar manner to controlling a motor with a translating piston (or a translating chamber and a non-moving piston, or even if both are moving, not shown).

Control means: turn on function, start, speed up, slow down, power on, stop, disable motor.
For the motor to function, it needs an electrical on/off switch to switch on the electrical system,
There is another switch which connects the starter motor to the electrical circuit and causes it to connect to the shaft and rotate.

On the same shaft that the moving piston or moving chamber uses, there may be a starter motor that utilizes power from a starter battery, which is itself loaded with electricity from solar energy. The starter motor rotates the shaft, so that it can start to rotate.
Input pressure control can be done as follows:
A
In a motor with a moving piston, the piston needs to be pressurized, so the pressure changes at the transition point where the maximum circumference changes to a minimum. This can be done electronically with a computer and a propelling jet. The pressurized fluid needs to be maintained, so the solution needs new solution.
New electronic-mechanical solutions Or it would be possible to create a mechanical solution, since the pressure changes are at a certain frequency, such as a camshaft communicating with a drive shaft through a time belt, which can press a flexible membrane communicating with said fluid, whose pressure needs to be managed.

To make this solution less complex, for example, instead of four subchambers a chamber containing one may be used, and the pressure only needs to be changed once.
A.A.
In a motor with a moving chamber, for example, five pistons need to be pressurized, resulting in a change in pressure at the transition point where the maximum circumference changes to the minimum. This can be done electronically using a computer and jets. The solution requires fresh solution since the pressurized fluid needs to be maintained.
New electronic and mechanical solutions In a motor with a moving chamber, for example, the internal pressure of five pistons must be managed in a different order from each other, but in the same order, and the pattern is repeated every time, so here too the camshaft solution , i.e. a camshaft communicating with the drive shaft through a time belt is possible. The cam disc can press a flexible membrane in communication with the fluid, which requires pressure management for each piston.
Translation AL power supply for motors based on the principle of Figure 11F
B
An even more reliable system can be obtained by a new principle according to Figures 11F and 13F for pressure management, i.e. by separating the fluid in the piston and the fluid in the closed space from the fluid in the recompression stage. can. That is, a change in the pressure within the piston can be obtained by a change in the volume of the closed space of the piston. Improved reliability may be associated with a reduction in the number of pressurized fluid transitions that can leak. In this principle, the control device can primarily use energy to change the volume of the enclosed space. This is a piston moving hermetically within a cylinder (e.g. a piston for the function of said piston, preferably a piston for speed/power, optionally a separate piston for power management). By using again the energy is reduced, said cylinders having successively different transition cross-sections and e.g. changes in the surroundings, such that a 65% reduction in the energy used is again obtained. , may be very well done. Also, because of this principle, embodiments with a fixed piston in the rotating chamber may be the best option to reduce energy usage. Although the circumferential diameter may be constant, the amount of reduction obtained will be small.
B
The change in pressure (and consumption) of the fluid within the expandable piston can also be done in alternative ways to the principle shown in FIG. 11A. By temporarily changing the volume of the sealed space of the piston, the output (torque) of the motor can be changed by adjusting the volume, and this can be done in series. It is a source of energy.

This is a more efficient way to use the available energy, and
In conjunction with the principle shown in A, the reliability of said motor can be increased. With this new principle, there is no leakage between the two parts of the connecting rod, the high pressure fluid when the piston is moving from the second longitudinal direction to the first longitudinal direction, and the low pressure fluid when the piston is moving in the opposite direction in the joint such as the crankshaft-big end bearing.

The energy used can be used to move a piston in a conical chamber that can be optimized to reduce the force acting on the piston rod of the piston to change the volume of the enclosed space. In addition, the energy used can be used to adjust the volume of the enclosed space in a piston-chamber combination similar to the one used for the volume change.

Movement of the volume-varying piston may be accomplished by using pressurized fluid to move the piston within the chamber from one point to another, or vice versa, by means such as a valve or other land control device. or by magnetic guidance. This is also valid for pistons regulating the volume of an enclosed space, the control of the movement of which can be performed, for example, by communicating with a human or computer-controlled speeder.
Rotary Power Supply for a Motor Based on the Principle of Figure 13(E) The change in pressure (and consumption) of the fluid in the expandable piston can also be done in an alternative way to the principle shown in Figure 12A. By temporarily changing the volume of the sealed space of the piston, the output (torque) of the motor can be changed by adjusting the volume, and this can be done in series.

The principle is that the siple is still more efficient with a rotary power source than with a transient power system, since there is almost no distance between the first and second rotational positions. The piston changing the volume of the enclosed space can therefore be guided by a cam disc attached to the shaft around which the motor power source rotates. In fact, this is the most efficient motor.

A motor having a circular chamber may have a wall that is parallel to the central axis of the chamber and that is at least part of the length* of the centerline of said chamber.
In the motor, the conical chamber (elongated or circular*) may be of the type such that the piston rod force generated by the actuator piston is constant, as is the case for any pump incorporated in said motor when the fluid is pressurized.

The chamber in which the actuator piston is arranged may include an internal convex wall of longitudinal cross-section proximate to a first longitudinal position, said cross-section may be divided upwardly from each other by a common boundary, two common boundaries; the distance between defines the height of the walls of said longitudinal section, said height being reduced by an increase in the internal overpressure rate of said piston, or in the direction from a first to a second longitudinal position. , the height of the cross-section of the common boundary may be determined by the maximum labor force selected for the common boundary.

If the piston is arranged in an internally tapered cylindrical chamber, the convex wall is concave. The piston-chamber combination may then include a cross-sectional boundary wall parallel to a central axis of the chamber. and the piston-chamber combination can include a transition between the convex wall and the parallel wall, the transition being a second
and at least a concave wall that can be located proximate a longitudinal position of.

The piston-chamber combination may also include a concave wall, which may be arranged from at least one side to a convex wall.
The various embodiments described above are provided by way of example only and should not be construed as limiting the invention. Without departing from the true spirit and scope of the invention, those skilled in the art will appreciate the variety of elements that may be made into the invention without departing from the true spirit and scope of the invention and without strictly following the exemplary embodiments and applications shown and described herein. Modifications, changes and combinations will be readily recognized.

All types of pistons, and in particular containers with elastically deformable walls, may be sealingly connected to the chamber walls during movement between longitudinal positions, engagingly connected to the chamber walls, or not connected; or may engage and sealingly connect to the chamber walls. Furthermore, it is possible that there is no engagement between any of said walls, and that the walls come into contact with each other. This occurs, for example, when the container is moving from a first longitudinal position to a second longitudinal position within the chamber.

The type of connection between the walls (sealing and/or engaging and/or contacting and/or no connection) can be achieved by using the correct internal pressure within the vessel walls, i.e. high pressure for a sealable connection, low pressure for engaging, and atmospheric pressure for no connection (production size vessels), therefore vessels with a sealed space are preferred as the sealed space allows the pressure within the vessel to be controlled from the outside position of the piston.

Another option for an engaging connection is a thin wall of the container, which may have reinforcements protruding from the surface of said wall so that leakage can occur between the container wall and the chamber wall.

In the case of actuator pistons connected to the main shaft by a crankshaft and where there are multiple actuator pistons all connected to the same main shaft, if the longitudinal positions of the actuator pistons are different from each other, the advantage is that the rotation of the main shaft of the actuator pistons is smoother and the "hesitation moment" for each of the actuator pistons can occur at other points in time when moving from the second longitudinal position to the first longitudinal position.

It may be necessary for all of the actuator pistons to be engaged or sealed to move from a second longitudinal position to a first longitudinal position within a chamber (which may change from one longitudinal position to another as it moves within the chamber), with the characteristic that the force on a second actuator piston rod (and thus the connecting rod from the actuator piston to the crankshaft) may be independent of the position the actuator piston has, in order to synchronize the force of each of the actuator pistons to the main axis (see reference "19620").

Feasibility studies have not previously quantitatively incorporated the lack of heat generated by the motor of the present invention compared to Otto motor types.
It is even more interesting and compelling than the motor of the present invention when heat losses are incorporated. Heat loss makes current Otto motors 25% efficient. First, assuming that the motor according to the invention does not generate any heat, the energy used to pressurize the fluid is between 5 bar and 10 bar (10 bar was already present in the pressure storage vessel when the motor was manufactured). It is possible to reduce this by approximately 65%. The overall efficiency of the motor according to the invention is less than 10%, i.e. 8.75%, due to the self-propelled actuator piston, which is unprecedented (David JC Mackay, Sustainable Energy Without Hot Air). The regenerative pressure pump shown in the present invention is
Another 65% energy savings when using the piston-chamber combination of the present invention again. Therefore, if we ignore that the heat is being generated by the pump, this gives a total energy usage of 8.75% x 0.875 = 7.6%. However, if part of the energy used for pumping comes from other sources, such as solar energy (solar power), flywheels, regenerative braking, etc., then the total amount of energy used is 10%
It may be less than

19611, as amended in 19618, added provisions to the description and conducted a feasibility study. The feasibility study had not previously quantitatively incorporated the lack of heat generated by the motor of the present invention compared to the Otto motor type.

It is even more interesting and convincing than the motor type of the present invention if the heat losses can be incorporated. Heat losses can give a current Otto motor an efficiency of 25%. In a first example, if we assume that the motor type of the present invention is able to reduce the energy used to pressurize the fluid by about 65% from 5 bar to 10 bar (10 bar was already present in the pressure storage vessel when the motor was manufactured), it can be assumed that said motor type does not generate any heat at all (isothermal). The total efficiency of the motor type according to the present invention is less than 10%, i.e. 8,75%, due to the self-propelled actuator piston, which is unprecedented (David JC Mackay, Sustainable Energy - No Hot Air - 2009). If the pump for regenerative pressure shown in the present invention again uses the piston-chamber combination type of the present invention, another 65% energy can be saved. Therefore, if we ignore that heat is generated by the pump, this is 8.75% x 0.875 = 7.6% total energy usage. However, if part of the energy used for pumping comes from another source (not from the total motor power), such as a battery charged by solar energy (photovoltaic power) and/or a fuel cell (e.g. H2), from a flywheel or a regenerative braking device coupled to a generator, the total amount of energy used can be reduced by 10%.
It may end up being less than that.

As previously concluded, the motor type configurations according to Figures 11F and 13F may be the most efficient (simple structure, near isothermal thermodynamics) and also the most reliable (no leakage), the configuration of Figure 13F being one that does not use crank generated rotation, and the configuration of Figure 13F would be used for quantitative evaluation of automotive motors.

In the present invention, we use the current VW Golf Mark II model RF, 1600cc, weight 836kg, and a 53kW /71 pk gasoline motor has four cylinders of φ81mm each and a pressure of 9 Bar, and a stroke of 77mm as the benchmark of the present invention. do. This gives a maximum force of 1159 N per cylinder, approximately 116 kg per cylinder. If all combustion parts are removed from the car body and aluminum is used instead of steel, it is expected that the weight will be reduced by about 50%. Therefore, the required amount per cylinder for driving the aluminum body is 58 kg, and it is possible to drive up to 4 passengers and luggage.

The chambers of the pump shown in WO2008/025391 have diameters of φ58mm to φ17mm respectively, with a maximum force of 260N (26kg) and a total stroke of approximately 400mm from 2 to 10 Bar. Using an expandable elliptical piston within the chamber, the actuator has worked very well. Thus, two of these chambers are currently used as part of the actuator.
This is equivalent to removing one cylinder of the VW Golf Mark II petrol motor, and all the parts related to combustion, which are currently made from aluminium.

The motor of the present invention changes the pressure in the enclosed space of the actuator piston from x bars (stroke: 2nd → 1st vertical position) to about 0 bar (stroke: 1st → 2nd vertical position). "x"
The value of can be chosen as small as possible in order to limit energy use. By using this special chamber type, the magnitude of the working force does not depend on the pressure value, so by using a pressure window, the pressure can be limited to 3.5 bar at the highest level and about 0.5 bar at the lowest level.

This starting point is carried over to the configuration of the pressure in the spherical piston placed in the rotating chamber of Fig. 13F, but with 31/2 bar in said particular chamber for part of the stroke (216,2 mm out of 400 mm). The chamber may be of simpler shape, as shown in Figure 13F. The force per actuator piston is max. 260N.

The change in volume of this sphere can be quite large:
V2 = 4/3 x 3,14 x 12,553 (φ25,1 mm; P2 = 0,35 N/mm2) = 8280 mm3 - V1 = 4/3 x 3,14 x 23,453 (φ46,9 mm; P1 = 0,05 N/mm2) = 54015 mm3 - with ΔV = 6,5 and ΔP = 7. The angle of the wall to the central axis of the chamber is L1 = 302,78 - 86,57 = 216,21, Δr = 10,9: angle = 2,9°, which is good.

The energy used for the "virtual" compression of the volume of said actuator piston at a first longitudinal position (index 1) into the volume of one cylinder at a second longitudinal position (index 2) is For a complete stroke:

Wisothermal = -P1V1ln(P2/P1) = 0.35 x 54015 x ln 7 = 0.35 x 54015 x 2,302585 x log 7 = 3678 Nmm/channel/piston/revs 36,8 J/channel/piston/revs 36,8 J The motor according to the invention does not have as fast a stroke rate as the gasoline motor (900 rv/m), because the actuator piston made of reinforced rubber is assumed to extend and retract more slowly. With 60 revs/min, this gives 1 revolution per second (15 times slower than the combustible motor). W= 36,8 J/channel/piston/s. There are 2x4 "equivalent" chambers (cylinders).

When using 5 pistons with an output of 294,3 J/s/piston and 0,295 kW/piston, one for each of the five subchambers (Fig. 13F) in the 360° channel, the generated power is 5 x 0,295 kW = The power will be 1,47kW.

Confirmation of the assumption of 1 revolution per second: with a 53 kW combustible gasoline motor, a saving of 92.4% is possible, as stated earlier in this study, and a saving of 7.6% allows only 4,03 kW to be used. In addition, if the number of revolutions per second is approximately (rounded off), it is assumed to be 3 revolutions/second.

Thus, a motor with 2×4 "corresponding" chambers, each with 5 pistons in 5 sub-chambers, rotates at 3 revolutions/second (=180 revolutions/minute), resulting in approx. Generates a power of 3×1,47 = 4,4kW. This would be enough to drive a VW Golf Mark II with an aluminum body.

Literature (David JC Mackay, Sustainable Energy - No Hot Air - p.127, Figures 20.20/20.21)
reveals a small electric vehicle that runs on approximately 4.8kW of electricity. This electric car comes from an 8×6V battery that can travel 77km on a single battery charge and has a charging time of several hours. If the energy is being generated from a battery that cannot be charged while the vehicle is in operation, this may be an option, but is not a preferred embodiment.

How much energy is required to pressurize and depressurize the actuator piston? Also, can you do it while driving?
It is necessary to force a pressure change on the actuator piston of the motor. We use the principles shown in Figures 11F and 13F.

Energy is derived from kinetic energy from the rotating chamber, for example in which the piston of a classic piston-chamber combination is moved by a camshaft communicating with the main motor shaft of the motor. When using the data used to calculate the motor power, change the volume of the enclosed space of the actuator piston by changing the "down" volume of the classic piston, rather than changing the pressure of the inflatable spherical piston. This can be done by letting

The volume change per stroke required by the actuator piston is achieved by the internal pressure change of said actuator piston from the second longitudinal position to the first longitudinal position, and therefore from a small sphere (φ25,1 mm) with a medium internal pressure (3,5 bar) to a large sphere (φ46,9 mm) with a low pressure (0,5 bar). The force is 260 N/stroke/piston, and regardless of the internal force, with 8 chambers made up of 5 pistons, the generated power is 4,4 kW at 3 revolutions/second.

The energy required to go from a first longitudinal position to a second longitudinal position is (FIGS. 14A and 14B):
1. By changing the spherical shape of the actuator piston (φ46,9mm; 0,5 bar) into the production shape (φ25,1mm; 0 bar (overpressure)) and contracting the actuator piston into the closed measuring space, we are increasing the volume - this does not consume energy if the friction forces between the pump piston and the walls of the confinement space are small enough.
2. The energy required to inflate a sphere (φ25,1mm, 0 bar) to (φ25,1mm, 3,5 bar) by reducing the volume of the enclosed space where the pump piston is approaching the actuator piston is:
Wisothermal = -P1V1ln(P2/P1) = -1 (check this) x 4/3 x 3.14 x 12.55 ³ x ln 4.5*/1 = -1 x 8280 x 2.302585 x log 4.5 = 12454 For Nmm/channel/piston/rpm and 2x4 chambers = 12.5 x 8 x 5 x 3 Js= 1.5 kW.
(*If P1 = 1 bar absolute, then P2 absolute is 4.5 bar.

Thus, the generated bruit power is 4.4 kW, the power required to drive the motor is at least 1.5 kW, and therefore about 2 kW is required, in addition to other final losses.

If a pump according to the above is present in the vehicle to access the motor, the current compressor has the following specifications: 220V, 170 1/min, 2,2kW, 8 Bar, pressure storage vessel 100 1. We need power at a lower pressure so that this improved compressor charges the pressure storage vessel a little faster.

At 8 Bar P = 2200 W, so at 31/2 bar you need to use the same recompression time as at 8 Bar. Only 3/8 x 2200 = 825 W. Even if the battery is a 24V battery, the current will be 825/24 = 34,4A. This is very large for a battery and therefore many batteries are available in the motor configuration diagrams. A, B, G and Fig. 11A, 12A, 13A
, the pumps with reference numbers 826/831 must be electric. Since it is only possible to charge these batteries by an external power source, the car would be disabled for hours. That is, the capacitor solution (Fig. 15E) is still in the research stage. It is not a preferred embodiment, but an option.

It would be better to avoid the conversion of power and use the motor configuration of FIG. 15C, where the pump 826/831 is in communication with the axle of a combustible motor, for example using H2, preferably produced by electrolysis and optionally by a fuel cell. The aforementioned process is powered by electricity from a battery charged by an alternator in communication with said axle.

825 W needs to be generated by the combustible motor. This is 24cc /66cc (VW Golf Mark II is 53kW, 1600cc, φ90mm, 4 cylinder → 825 W is about 24cc, 90mm cylinder, or if it is 3 times faster, about 2,2kW is about 66cc, 90mm cylinder) Classic It may be a motor, which can be compared to the large-scale prime movers currently in use. For several months now, mopeds have been shown on television that electrolyze water, store it in a tank (originally for gasoline), and use the resulting H2 in the combustion process, but this is possible. The car is an external motor of this size, and the extra combustibles that previously took off the VW Golf Mark II will unfortunately have to be replaced with the motor. This means there is no pollution or CO2 emissions,
Noise can be well reduced with appropriate noise mitigation measurements, and this feasibility study can There is a possibility that it will be established.

A motor based on a crankshaft solution (FIGS. 11A-D and 11F) with an elongated chamber and a piston connected to the crankshaft by a piston rod/connecting rod can preferably be used as the main motor of a transport vehicle, e.g. a vehicle. The wheels or propellers can be connected to a central main motor by a drive shaft and a distribution device such as a cardan. Alternatively, the motor type can be used as an eccentrically positioned motor, which can be directly connected to each of the propulsion devices such as wheels or propellers.

A motor based on a chamber arranged around a circular central axis and a piston increasing or decreasing its size (Figs. 12A-C, 13A-G) is preferably used as an eccentric position motor in a transport vehicle, e.g. may be used. Each of the motors can be directly connected to each of the propulsion devices. Optionally, it may be a central motor that may be connected to the propulsion device by a drive shaft.

Control of the motors is preferably performed by a computer, especially when each motor is directly connected to one of two or more propulsion units used by the transport vehicle.
A flywheel is provided, preferably connected to the main central motor and optionally eccentrically located on each propulsion device. The flywheel can be used to energize one of the pumps (e.g., 818, 821, 821', 826, 826') (see, e.g., Figs. 11A, B, C, F, 12A, C, 13 A, B, E, F) in communication with a pressurized storage vessel (e.g., 814, 839, 890, 889), to maintain smooth motion, or to recover energy for acceleration after braking the transport vehicle (and simultaneously store the motion braking energy). All or a few of the above types of flywheels can be present in a transport vehicle equipped with a motor according to the invention.

Another aspect of recovering energy during braking may be a pump connected directly to the main shaft, which may be a central drive shaft (e.g., References 821, 821'), which can pump fluid to much higher pressures and transfer the resulting high pressure fluid to a pressure storage vessel (e.g., References 814, 839, 890, 889).
Optimal Configuration of Chambers for 19617 Actuator The geometry of a chamber that is optimally used in cooperation with an actuator piston may differ from a chamber intended for optimal use in a pump, as the operating conditions of the actuator and pump may be different.

For example, an actuator piston must provide maximum force by using as little energy as possible while moving at a suitable speed. Also, in the case of an actuator piston in communication with the crank, the sub-conditions may be different from, for example, the sub-conditions of an actuator piston in communication with the rotation chamber, for example the point at which the maximum force is required.

In order to use the actuator piston as a self-propelled piston, the elongated chamber must be of a type in which the walls of said chamber flare outwards when moving from the second longitudinal position to the first longitudinal position. There is. Therefore, the angle of the wall with respect to the central axis of the chamber from the second longitudinal position to the first longitudinal position must be positive. This angle may fix the speed of the actuator piston. And, of course, the transition from one point of the wall to another in the longitudinal direction needs to be smooth, thereby limiting the friction between the actuator piston and the wall of the chamber.

The expandable actuator piston itself needs to have internal pressure to be able to load the chamber walls. In order to move said actuator piston, the center of the flexible wall must be first than the circumference that engages and connects the wall of the elongated chamber.
It is necessary to be close to the longitudinal position of. The greater this distance, the faster the speed of the actuator piston within the chamber.

The reaction force of the chamber wall on said actuator piston fixes the force with which the piston pushes the chamber wall in the first longitudinal direction, and therefore the force on the piston rod is also assembled when at least one cap of the actuator piston, the cap closest to the second longitudinal position, is assembled on said piston rod.

Article 19620 of this patent application shows a chamber which, when used in a pump, reduces the piston rod effort by about 65% at 8-10 bar of pump fluid (e.g., Fig. 21A), which is excellent for pumping purposes. This reduction should be seen in comparison with the effort required in a straight cylinder, and follows from the following comparison:

A classic high pressure bicycle pump and an improved bicycle pump in which the chamber has the shape of Fig. 21A. In said chamber is a maximum force that is almost independent of the pressure of the fluid in said chamber and is therefore almost constant during the pumping stroke (e.g. from 2 bar when the maximum force is reached).

The same chamber used in the actuator containing the 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. That is, the price to be paid can be more favorable than that when the maximum pressure is reached in a straight cylinder with a constant diameter, the working force is approximately 1/3 compared to the working force (same as above comparison source). The magnitude of the force may not be suitable for actuator piston purposes, but in addition, the constant force may also not be suitable for use with a crank.

This is also effective when the chamber is circular (circular) rather than elongated. In certain solutions where the actuator piston is stationary, the actuator piston placed within the rotational movement chamber may use a chamber type as described above. Such a chamber may be necessary if multiple pistons are used, e.g., five pistons (e.g., FIG. If different, the force exerted by each piston may be the same for all pistons, so that none of said pistons pushes on the other and the total force is the same as that of only one piston used. This is five times the case. Depending on the purpose, gears may be required to obtain the required torque and speed.

Other optimal configurations for the actuator chamber are possible.
The parameters of the elongated chamber in which the actuator piston is connected to the crank are:
A relatively short length L of the chamber allows the force F(p,d,μ) to vary during the stroke from the second to the first longitudinal position, so that a maximum force is obtained when the actuator piston has almost reached the end of the first longitudinal position (where F=force from the piston rod; p=pressure in the actuator piston; d=diameter of the chamber at a certain longitudinal position; μ=coefficient of friction between the wall of the chamber and the flexible wall of the actuator piston).

The friction force F(μ) throughout the return stroke is zero, obtained by lightly siphoning the overpressure on the actuator piston [F(μ)=friction force between the walls of the chamber and the flexible wall of the actuator piston],
The velocity v(φ, F) should be optimized over the length L of the chamber (where v=velocity of the actuator piston relative to the chamber; φ=angle between the chamber wall and the central axis of the chamber; F=force from the piston rod).

Therefore, the pressure drop (ΔV) when the actuator piston is moved from the second vertical direction to the first vertical direction while changing the volume needs to be made as small as possible while the closed space is temporarily closed.

The parameters of a chamber whose walls are arranged around a circular central axis, the center of which is located on the center of the main motor shaft, said chamber rotating, and two or more actuator pistons are present and stationary and engaged with said chamber walls, in addition to the chamber of FIG. 21A:
It may have a circular cross-section.

The circumference of the chamber wall must be the same regardless of the distance to the center of rotation, which can affect the cross-sectional shape of the chamber.
Frictional forces should be optimally reduced by using improved lubricants such as superlubricants that have a much lower coefficient of friction than other lubricants, for example, that work well with rubber and metals such as steel and aluminum.

However, it may be necessary to manufacture an optimum configuration of pistons to achieve the effect that the circumference of the chamber walls must be the same regardless of the distance to the center of rotation, and it may be necessary to manufacture an optimum configuration of pistons to achieve the effect that the circumference of the chamber walls must be the same regardless of the distance to the center of rotation.
19617 19618 Thermodynamic Problem When a fluid in a system (an elongated chamber with an actuator piston in communication with a crankshaft - a chamber that may be arranged symmetrically around a circular central axis that may be in communication with the crankshaft or in communication with the main shaft of a motor) is compressed, heat can very well be generated.

The storage of fluid in the pressure storage vessel may be arranged while the device in which the motor is used is being manufactured. While the motor is running, a smaller portion of heat may be generated in the storage vessel when the higher pressure fluid from the last pump of the pressurization cascade enters the fluid in the vessel, which may have a lower pressure (Figs. 11A-C, 12A-C, 13A-B).

The pressurization of the fluid obtained from the third enclosed space of the motor type using a crank assembled on the main shaft of said motor generates a very large part of heat in the first pump of the pressurization cascade, which can receive its energy from the main shaft, and another part of heat, approximately the same size, can be generated in the pump that can obtain its energy from other energy sources (preferably any sustainable energy source such as solar cells, fuel cells, electric batteries loaded by solar energy, or, if necessary, classical energy sources such as electric batteries loaded by a generator in communication with a combustion engine) (FIG. 11A).
~C, 12A).

The actuator piston takes both the pressurization in the closed space + the cavity in the actuator piston body from the second closed space and expands into the third closed space. The pressurization can be slightly greater than the expansion, so the actuator piston can get a higher temperature than it did when the motor started (Figures 11A-C, 11F, 12A-C, 13A-E).

This system therefore generates heat and can be used, for example, to heat the cabin of the vehicle or to heat a third closed space in which expansion takes place (adiabatic). This cannot be easily done as it is located on the crankshaft. This is therefore a more or less non-adiabatic situation.

Of course, it is better to compensate for the heat generation. Where heat is generated, we have isothermal conditions. If the pressure change in the actuator piston is controlled by a piston moving in a bidirectional pump chamber, which is actually the closed space of the actuator piston, then by changing the volume, both compression and pressurization occur in said chamber, so that heating and cooling are balanced. This is the combination of a non-moving actuator piston and a moving (rotating) chamber (Fig. 13F-G). The (theoretical) efficiency is close to 100%, so again from a thermodynamic point of view, this is the most efficient motor principle.
19617 modified 19615 energy source working in concert with the motor in 19618/19627.

The motor can be operated with any other energy source, preferably sustainable, but optionally non-sustainable. Such an energy source is needed to supply about 7.5% of the motor, which may be the limit of efficiency improvements associated with classical motors burning fossil fuels, for example by using an Otto cycler.

Sustainable energy sources such as solar, hydro, wave power, and other energy sources that do not produce unwanted chemical emissions such as CO, CO2, or NO when energy is produced.

In the case of the motor according to the invention, the energy source is preferably charged by e.g. electric power, a capacitor (= electricity stored in a very large capacitor) or sunlight, e.g. with concentrating means (mirror). or without photovoltaic solar cells, or fuel cells, e.g. air cells with H2, or any kind of electric cell charged by compressed air, such as with potential hydraulic energy. Good too. H2 fuel cells can be "charged" with H2 obtained from the electrolysis of H20. This can be stored in containers. Electricity is obtained from a special battery (no starter battery) that can supply energy continuously. This battery is charged by an alternator and communicated from the motor shaft and/or solar cells. Hydrogen can also be stored in special containers and inserted directly into the fuel cell.

Any energy source burns electricity, a compressor driven by a capacitor or any type of electric battery, or a motor, loaded by a generator that is turnaround based on steam produced by a fossil fuel burner It may also be fossil fuel, etc.

A motor according to the invention can have one energy source or a combination of energy sources, preferably sustainable, optionally sustainable and non-sustainable.
When used as a motor in transport devices such as ships, trains, vehicles or airplanes with limited possibilities for connecting to larger energy sources, the battery may be temporarily charged by an external energy source, for example via an electric cable. The filling of other energy-containing materials, for example H2, can be carried out by hoses etc. Thus, by a suitable temporary connection to said external energy source, charging the energy-carrying material placed in said device.

Preferably, the device is self-sustaining and can be moved over strategic distances without prolonged external charging from an external available power source (eg, electricity). There are several definitions of strategic distance. For example, in the case of a commuting vehicle, 2 x 50km commuting + 40km per day
A random distance of , without filling, is sufficient. For example, vehicles used to travel longer distances may need to travel 500km, or even twice that distance, without refilling. The last thing I mentioned is the limit of what humans can accomplish in a day.

Preferably, a mobile power source (e.g. battery, fuel cell, electrolysis of H2O resulting in available H2 for combustion purposes, pressurized fluids, or other possibilities not described here) mounted within the transport device is capable of being self-sustaining for at least one day. Preferably, it is also possible to travel overnight. The power source preferably does not add much extra dead weight (increased RAT), which is particularly important for the vehicle, although this may not be crucial for efficiency.

There are several battery types, the latest ones have high power and are efficient, but they take up more weight and space. They take a long time to charge, but rapid replacement of batteries is not possible, as it requires infrastructure. On the other hand, new and old batteries cannot be separated. Charging from solar cells and/or solar panels is not enough for energy utilization (see feasibility study). A plug, a connection to the power grid, an available infrastructure, is required.

A "battery" that uses a suitcase-sized capacitor to reduce charging time to a minute or two and then controls the re-discharge of electricity to the motor system could be a solution to all the problems mentioned above while still using batteries. It is still under development in the US.

Fuel cells are not cheap and may not be very efficient at generating electricity, but they do not add up to much extra weight. This differs from conventional methods, where a combustible (fossil) motor is in communication with an alternator, for example, the hydrogen required may be a safety hazard. Also, storage of hydrogen may be difficult due to leakage from the container. For other substances, there is no leakage. An electrical distribution infrastructure may also be required, but home-based electrolysis systems already commercially available produce hydrogen for their own use by electrolysis. However, after seeing in 2009 a combustible motor (<50cc) with H2 obtained by instantaneous electrolysis of water, said water contained in a tank where gasoline is usually stored, this can also be done for this motor according to the present invention. The electricity for electrolysis may come from a battery designed to be used.

The equipment (in constant use) may be charged by an alternator using the rotational kinetic energy from the motor, while the electrical power is additionally charged, for example by a solar cell.
The electricity generated by the fuel cell, for example H2, can be used to charge the battery, and the generated electricity can be used for motor function. An alternator is in communication with the main shaft of the motor and can additionally charge batteries, such as the constant use battery and a possible current starting motor battery, for a possible current starting motor. A solar cell can be added to charge the battery. For example, the electricity generated by a fuel cell using H2 can be connected directly to the motor function, bypassing the batter(y)(is).

Other possibilities include, for example, that H2 is used for flammable purposes, for example to rotate an axle that is combined with a crankshaft and communicates with an alternator, said alternator charging a battery. A classic piston-linear cylinder motor is mentioned.
The alternator may also be directly connected to other motor functions by wires. The power of the combustible motor depends on the complement demand for power, so the motor according to the invention cannot produce anything. The power of said combustible motor, if used 100% for motor function, may be very small compared to current combustible motors, which allows for example electrolytic processes to generate H2. , it becomes possible to make it mobile, for example for use in a car.

What is required of the invention is that a bidirectional pump, e.g. for changing the volume of an enclosed space of a stationary spherical piston, disposed in a rotating chamber, e.g. It is possible to use an electric motor to turn the wheel around an axle that communicates with a crank that requires electricity. The axle may for example be the main axle of the combustible motor using H2 as fuel.

Another configuration can have the same configuration as the overall solution described above, if the pump is used for fluid recompression and is used to control an actuator that controls the pump.

Another configuration can be used without the use of electricity to change the volume of the closed space when the pump is replaced by the camshaft, electricity is not needed only for the starter motor, but is obtained from a starter battery, which can be charged by an alternator driven by the main shaft of the motor and/or by a solar cell. The camshaft solution can preferably use several pistons, optionally one piston. Small pumps mean higher pressure in the actuator piston, driven by the main shaft or by an electric motor that receives its energy from a battery, and are necessary for the higher speeds designed to be used all the time.

A tank containing conductive water can be filled from an external store of water, and if the water is not conductive, conductive material can be added so that the water is becoming conductive.
The pressure reservoir may be pressurized by a cascade of pumps but also, optionally, by an external pressure source through a pluggable connection (reference number 2701 in the respective figures).

The battery may be charged by an alternator, solar cell, or/and H2 fuel cell, or, optionally, by an external power source via a plug connection. (Reference 2700 in each drawing)
The piston and the chamber may both rotate about a midpoint about which the chamber rotates.

The present invention can be constructed with less weight than those based on conventional piston-cylinder combinations. Because the motor can function in the dark, a complement or addition to the solar cell may be necessary. This is for example any other sustainable power source, such as a fuel cell, for example of the H2 type, which reacts with O2 in the atmosphere and gives electricity and H20. The fuel cell may require a relatively small storage vessel, which may be under reduced pressure. This means that you may have an h2 power distribution system at home, or your power distribution system may not be very dense.

In motor types where the enclosed space is in communication with the recompression cascade of the pump, electricity can be used to energize an electric motor driving a piston pump through a separate crankshaft, this can be done as a complement to solar cell energy, for example when it is dark, and can also be done at any time.

In addition, a generator of this type can be added to this type of motor, which can be driven by the main shaft and can load the accumulator.
In motor types where the fluid in the confined space is separated from the recompression cascade, electrical energy will likely be required for valve control. This may increase the need for other sustainable power sources, such as fuel cells as mentioned above, rather than solar cells.

It can also be used for an external cascade system, not yet added in Fig. 11F. Fig. 13F may be required for recompression of the pressure vessels 1063 and 889, respectively. This can be done by a cascade of pumps, at least one of which is in communication with the main shaft and at least one of which is in communication with an external power source. The pumps can be in communication with the pressure vessels. For the solutions in Fig. 13F, a pump may also be sufficient.
19617 - Gearbox - 19618 - Clutch The motor of the present invention may have a certain maximum for the number of revolutions (rpm) limited by the change in shape and/or pressure at both the transition points from the first circular point to the second circular point (first and second longitudinal positions) when the piston is traveling in an elongated chamber or when it is traveling in a circular chamber. The flexibility of the expandable piston is key, i.e. its walls, e.g. made of rubber, i.e. the hardness of the rubber and reinforcing layers, as well as the number of reinforcing layers used and the angle between the reinforcing layers if more than one layer is used (see chapter 19650).

The motor according to the present invention is a two-stroke motor when the piston is operating in an elongated chamber, where 1/2 revolution = power stroke and the other 1/2 is the return stroke. In a feasibility study, when compared with a 4-stroke, 4-cylinder, 1595cc VW Golf Mark II gasoline motor with an idle speed of 700-800 rpm and a maximum speed of 2500 (checked) rpm, the equivalent speed of the motor according to the present invention was determined according to the feasibility study. It may be half of the above to generate the same power as the configuration. This reduced speed is compatible with the motor according to the invention.

When the clutch begins to engage the flywheel, the reduced speed limits the impulse on the main motor shaft. The feasibility study shows that if the torque per kg of vehicle weight is the same, the above Golf Mark II - 50% reduction in the net weight of the vehicle according to the invention can now be considered if the configuration is maintained. I found out what I can't do.

If a gearbox (manual, automatic, e.g. Van Doorne's Variomatic® or a general automatic gearbox with fluid) is used, the ratio and the number of gears may differ from the number of gears currently used in the vehicle. The last mentioned concerns a specific characteristic of a combustion motor (limited function window in terms of the rotational speed of the main motor shaft) that is not present as an essential part of the motor according to the invention. The aforementioned gearbox preferably has an automatic gearbox, optionally a manual gearbox, if a gearbox is required.

The quantitative considerations are as follows.
- Wheel diameter φ0.65m (VW Golf Mark II),
- Motor idle speed: 350-400 rpm, Motor drive speed: 2x idle speed Therefore,
60km/h: Motor 750 rpm
Wheel: 490 rpm, Gear ratio: 1:1.5 lowered

90km/h: Motor: 1000 rpm
Wheel: 735 rpm, Gear ratio: 1:1,35 lower
120km/h: motor 1250 rpm
Wheel: 980rpm, Gear ratio: 1:1,28 down
140km/h: Motor: 1500 rpm
Wheel: 1143 rpm, Gear ratio: 1:1,31 Downward (Conclusion)
- If reverse traction was not required, the gearbox was not required, thus reducing weight further.
The revolutions per minute still seem too high to change the shape of the expandable piston, and if this proves correct, a gearbox may be necessary - if so, a relatively slow rotating motor may be needed to increase the revolutions, i.e. to be able to use these revolutions, so that the motor can be coupled to the wheel by a clutch. For normal size wheels, it would be necessary to gear down again.
Motor Sound of 19617- The pitch of the sound of the power section of the motor according to the invention is very low due to the absence of explosion and can be significantly different from the commonly known engine sound of a gasoline motor based on the Otto motor design (see Classiccars, Issue 402, February 2007, pp. 86-89, "Why engines sound good"). Instead, a lubricating (e.g. Super Lube) friction sound of the expandable rubber piston body on metal or plastic from the chamber can occur. This sound can be of low frequency.

In the design of the elongated chamber, the pitch of the sound (from the second longitudinal position to the first longitudinal position)/
Only frequencies that are silent (from the first longitudinal position to the second longitudinal position) are used, but sounds always occur in the circular chamber design. These are also fricative sounds, so the sound frequencies may be low.

The motor of the present invention is a two-stroke motor (remember the green motor), but most current automobile motors are four-stroke motors, so to obtain the same or equivalent power output, the number of revolutions per minute of the motor of the present invention can be half that of the motor of the Otto design. It can also reduce the number of revolutions per minute and add low-frequency sound.

In addition, there is sound from the pump (compressor) that generates the recompression pressure of the pressure vessel. In the case of the piston chamber type of the present invention, the pump can generate noise from the valves, the discharge of fluid from the chamber into the pressure vessel, and the suction of depressurized fluid, depending on the type of motor repressurization shown in the figure. be.

Current air compressors, which are based on pistons that move inside long, narrow chambers, sound downright unpleasant. These sounds can arise from the fact that the speed of air can exceed the speed of sound, and therefore shock waves are a source of discomfort.

In a design according to the invention, it is preferred that the velocity of the fluid is lower than the speed of sound, and as an option, for example a contrawave design (e.g., even if the motor is of the combustible motor type, the Audi ) attenuates the shock wave from the excess air velocity wave.

In the recompression type according to the diagram, there are no valves for introducing pressure changes and the piston-chamber combination is redundant. This motor type is not only the most efficient according to the invention, but also the quietest of all motor types.

The generation of electricity to (re)charge the battery that runs the pump may repressurize the pressure vessel, which may correspond to the main motor section pressure, but may require an Otto motor (equivalent to a prime mover) of about 60cc on H2, preferably as motive fluid, optionally gasoline/diesel or other flammable fluid (see feasibility study). The sound of such a prime mover is usually garish, but is tolerable if the sound is well damped.

Therefore, the total sound of the motor according to the invention is not zero as in the case of electric motors, but a low-pitched, low-frequency sound. This makes it possible to identify a car by its sound, which is better than cars with only electric motors that drive at low speeds.

The low frequency can be changed if it is concluded from the working prototype that the low frequency is:
19627 SUMMARY OF THEINVENTION In a first aspect, the present invention relates to a piston-chamber combination, the chamber including a wall with a cross-sectional boundary parallel to a central axis of the chamber, the chamber including a second chamber communicating with the first chamber via a channel with a longitudinal direction, the wall of the second chamber parallel to the central axis of the chamber having a concave cross-section.

For example, the conical chamber of the improved bicycle pump may be divided upwards into longitudinal sections, the common boundary of which is defined by the overpressure (e.g. atmospheric) rating that the piston can produce, e.g. 1 bar, 2 bar, 10 bar, etc., moving from a first longitudinal position to a second longitudinal position of the chamber, the chamber having convex and concave longitudinal cross sections, the cross sections being divided upwards from each other by a common boundary, the height of the walls of the longitudinal cross sections decreasing with increasing overpressure rate, and the lateral length of the cross sectional common boundary being determined by a maximum working force selected constant at least near the second longitudinal position relative to the common boundary.

Another factor determining the appropriate shape of the longitudinal cross-section of the chamber is sufficient space to have the piston in its bottom position (second position) with respect to properly sealing the piston to the walls of the chamber. For example, if the chamber is designed to reduce the acting force, the smallest at the point of highest pressure, as in WO/2008/025391 where the smallest part of the chamber is φ17 mm. The area of the longitudinal cross section is that the piston can be moved.

The longitudinal section may have convex and/or concave surfaces. The part of the chamber where the convex end and the concave wall begin and meet the conical base is used in bicycle floor pumps to keep the convex/concave parts of the chamber at a constant ergonomic height so that pumping is comfortable for the user (WO/2008/025391).

The spring force actuated piston, e.g. a flexible inflatable inflatable container piston (e.g. EP 1 384 004 B1), is capable of starting to move on its own from the second longitudinal position to the first longitudinal position. and the cross-sectional area and circumference of the second longitudinal position are smaller than the cross-sectional area and circumference of the first longitudinal position, and a sealing pressure exists from the piston to the wall of the convex/concave chamber wall, and the piston and The longitudinal component of the frictional force with the chamber wall is smaller than the longitudinal component of the sealing force. In order for the piston rod to maintain a position controlled, for example, by the user of a bicycle pump, it may be necessary that the wall of the chamber in contact with said piston be parallel to the central axis of the chamber. This parallelism provides a sealing force that does not require longitudinal components, so the piston, which is sealed to the chamber wall only in the position desired by the user, remains in that position. For example, EP 1 179 140 B1 shows a chamber in which at the top (first longitudinal position) and at the bottom (second longitudinal position) part of the inner wall of said chamber is centered. parallel to the axis and therefore where the piston rod is located when the pump is not in use, or where the piston rod is changing its direction, i.e. at the top of the chamber by the user when the pump is in use. This is the last thing mentioned that occurs in The reasons for the parallelism of EP 1 179 140 B1 are not disclosed.

Movement of the piston type from a second longitudinal position to a first longitudinal position within the chamber may occur when the piston is engageably movable or when the piston is sealingly movable within the chamber. is possible when it is possible to move to

In a second aspect, the invention relates to a combination of a piston and a chamber. The chamber has an outlet between a convex wall and a concave wall, the outlet being in communication with a hose. The longitudinal section may have a convex and/or concave surface. The convex shaped end and the part of the chamber where the concave wall may begin are used in two-wheeled floor pumps to keep the convex/concave shaped part of the chamber at a constant ergonomic height, and the pump is comfortable for the user (WO/2008/025391).

When the base is hollow it can be used in three ways.
Optionally, this portion is left open and an outlet is added at a second longitudinal position of the chamber, said outlet preferably being in direct communication with a hose.

Optionally, the outlet comprises a check valve, the check valve communicating with an expansion chamber contained in the bottom of the chamber. The problem is that such an expansion chamber may be negative only for higher pressures, regardless of the pressure, rather than slowing down the pump at lower pressures, the volume of said expansion chamber is expanded. This is something that will happen. Such a solution is necessary if the piston gets stuck in the concave transition from the convex wall to a further longitudinal position of the chamber, or if the piston is too large to move into the longitudinal position. be.

In a third aspect, the invention relates to a piston and chamber combination. The concave inner wall is located between at least two common boundaries. Preferably, the hollow part can be used as an additional pumping volume of the chamber, and the piston must be able to move towards the bottom without hindrance. What is needed is a smooth transition of cross-section from a convex wall, said transition comprising a concave wall. Depending on the height of the cross section and therefore the pressure velocity - these concave walls may be located between at least two or more common boundaries, the last mentioned at high pressure. If there is insufficient space near the second longitudinal position for the piston to move, there must be sufficient space for the piston to move at that position.

In a third aspect, the invention relates to a piston-chamber combination, comprising said second chamber, including a third chamber communicating with said second chamber through a check valve. Thus, on the wall surface of said chamber, counted from a first longitudinal position, the convex shape of the side of the longitudinal cross-sectional area must be transferred to that part of the bottom chamber, where the wall of the chamber wall is parallel to the central axis. For this, a transition from convex to concave is necessary for a smooth transition, and therefore the shape of the side of the longitudinal section at the transition must be concave in the direction from the first longitudinal section to the second longitudinal section. If the piston has a certain longitudinal length and has a seal with such a longitudinal length that the seal cannot fit the transition from the convex side of the longitudinal section to the concave, the solution is to close the chamber there, create an outlet by means of a check valve, and use the remaining chamber as an expansion vessel. This is useful for proper pumping at high pressure. The location of the common boundary is at a different length than the first longitudinal location, but the distance between the common boundaries is different, and the swept volume of the pump having an expansion vessel is smaller than the swept volume of the pump using the base as part of the swept volume.

In a fourth aspect, the invention relates to a combination of a piston and a chamber, said chambers being separated by an open fourth chamber, said chamber having an outlet, the outlet terminating in said fourth chamber, said fourth chamber being a basic chamber and nothing more, said chamber may have an outlet which is a nipple.

In a fifth aspect, the invention relates to a piston and chamber combination, the outlet of which is in communication with a hose. To optimize the pump speed, the hose of the bicycle pump is expandable under a certain pressure, so that an expansion vessel is formed there. That is, the pump pumps very efficiently at low pressures where the hose does not create an expansion vessel. Such a pressure vessel creates more volume compared to the volume of the tire pumped compared to the volume of the tire alone. Most of the pumping is done for low pressure tires. The expansion of the hose may be limited by a reinforcement of the hose, and the expansion may take place only in a part of the hose. The piston may be engageably movable relative to said chamber wall. The piston may be scalably movable relative to said chamber wall.
19616-19620-19627-Added: The use of the chamber of Fig. 21 A used in an improved bicycle pump can reduce energy use by approximately 65% at pressures of 8 to 10 bar compared to current high pressure bicycle pumps. This is calculated as follows:

The chamber of FIG. 21A is designed so that the maximum force is 260 N at any pressure, particularly at the higher pressures, thus 8 or 10 bars.
The current high pressure pump consists of a straight cylinder with an inner diameter of φ27 mm, so the force acting at 8 bar is F = p×O = 0.8×0.25×3,14×272 = 458 N. At 10 bar: 572 N
At 8 bars the payout is 458-260/458 = 198/458, so the payout is 43%, at 10 bars it is 54%. At 12 bars it is 687-272*/687 which is 60%, at 14 bars it is 801-318**/801=66%, at 16 bars it is 916-363"7916 = 60.3%.

The efficiency of the improved bicycle pump is much higher than current high pressure bicycle pumps, which influenced the selection of 260N as the maximum force. However, if a φ17 mm straight pipe section is also used, in addition to the conical section of the chamber, the pump pressure was designed to be higher than 10 bar. F is 12 bar: 1,2×0,25×3,14×172=272N*, F is 14 bar: 318N**, 16 bar. 363N***.
(Conclusion):
The 65% mentioned at 8-10 bar should have been 54%, but the chosen maximum force of F = 260N affects the result, so it is optimized for bicycle pumps, but now especially It might be good to recalculate the chamber for use with motors.
19617- The elongated conical chamber design added to 19620- in European Patent Application No. 100754027 (08-09-2010), Figures 21A, 21B, 22-25 (inclusive),
It is designed based on the following mathematical considerations.

The shape of an elongated conical chamber of a pump having a central axis is a line connecting a certain dot (x coordinate: along the central axis, y coordinate: perpendicular to the central axis) to the outside of the central axis. The chamber has a different cross-sectional area and has a first and a second longitudinal position, the first longitudinal position has a larger cross-sectional area than the second longitudinal position, the piston moves between the pistons, the pistons are sealingly connected to the walls of the chamber and have a production size corresponding to the circumference of the second longitudinal position, and the pistons have a predetermined maximum working force due to the shape of the chamber. The position of the dot relative to the central axis is determined as follows:

When said piston is moving in an elongated conical chamber from said first longitudinal position to said second longitudinal position, the remaining volume Vx is e.g. The remaining volume Vx is defined as the volume of said chamber at the position Lx measured up to the longitudinal position (0 point), Lx, and if there is an overpressure Px, the overpressure Px is used in this calculation. Counted relative to standard pressure, e.g. atmospheric pressure.

Vx = 3,14.[0,00046. ^Sx3 +(1,118-0,00139.L). ^Sx2 + (900-2,236.L + ^0,00139.L2 ) Sx]
here,
Vx is the remaining volume at standard pressure Px= z Bar where Vx = V0/(z+1)
V0 = the total volume of the conical chamber, where S = L is the total length of the conical chamber
Sx = Step in the iterative calculation process
The longitudinal position where Px = z Bar (z) occurs within a given pressure window (e.g. 1 - 10 Bar overpressure) can be calculated iteratively using steps S (which, if computer software is not available, to overcome the calculation of third degree equations), where step S is a fraction (e.g. 1/1000) of the total length L of said conical chamber, counted along said central axis, and Sx is found from said equation, giving the x-coordinate of said dot as Sx. L.
If the chamber includes a non-conical member (eg, as seen in Figures 21A, B), then only the projected length of the conical wall on the central axis need be used in calculating L and Lx.

The y coordinate of the dot is determined as follows.
When a specific maximum acting force Fmax is selected, the position of the dot at a specific longitudinal position Lx on the central axis can be derived from the selected 0 point as follows.
Dx =√ Fmax /0,008.Px (Px is in bar, D is in mm, F is in kgf)
the y-coordinate of the dot from the central axis at the longitudinal position Sx; L is Dx/2 as in the previous figure if a laterally symmetrical chamber design is chosen.

The shape of the chamber wall is larger than a line passing through all the detected points: in fact, if it is drawn as a set of line segments, it is possible to smooth out ("pedichis") said set of line segments, resulting in a continental shape of the chamber wall.
Deformable Fluid The use of the fluid in the actuator piston is as follows.
1. A gaseous medium, preferably air or N2, for the CT pressure management system;
2. Combination of gas and liquid,
3. A liquid system for ESVT pressure management, preferably hydraulic oil or H2O. The use of liquid can give better economy to pressurize the actuator piston by moving the volume of liquid to or from the actuator piston by a pump. The opposite (de)pressurization of a gaseous medium can occur.

Also, the reduced pressure of the heated gaseous medium can lead to icing of the actuator piston walls. This can also affect the lubrication of said actuator piston with the chamber walls and therefore the efficiency.

Since liquids are incompressible, pressure can build up at the very end of the pump piston's trajectory. This works fine for a fast rotating camshaft or crankshaft, for example, as shown in Figure 90L.
Therefore, when using closed space volume techniques, liquids are preferred as the deformable fluid.
19630--Circular chamber design invention summary The circular chamber shown in Figures BC and 14D, in which the chamber may move and the piston may not move, is divided upwards, for example, into four identical sub-chambers. These chambers are arranged so that the effect of each is obtained, so that the circular force of each piston, having a different position in each of its circular sub-chambers, may be the same on the chamber walls. This is to avoid unnecessary friction, which reduces efficiency, and increases wear on the pistons. The chambers may have a constant circular force, and therefore a constant torque. The size may depend on the pressure.

Therefore, there is no need to update the annular chamber to multiple chambers to accommodate multiple pistons. However, the wall angle of the sub-chambers is larger than that of the one chamber that has the same circle as the central axis. Therefore, the force in each chamber is greater than if a single chamber was used for multiple pistons.

The chamber shown in FIG. 12B may have a moving piston or a stationary chamber, but may in fact have the same basic design as described above for the figure. 13C and 14D. The piston may have a constant circular force on the chamber wall.

The subchamber is configured such that the chamber comprises two circular sections within a circular cross section. Each circular section has its own center point located in the opposite quadrant around and at the same distance from the center point of the circular central axis of the (sub)chamber. The circular portion may be located around the central axis of the chamber and may be circular.
SM-PVT1
In the final version, compared to the cross-section of the elongated chamber in Fig. 21A/B, a (virtual) common boundary line (9,11, 13,15,17,19,21,23,25,27), the common boundary line in the longitudinal section of the circular chamber is expected to converge with a line drawn from the furthest boundary. Ru. of said chamber in cross-section up to the center point of said circular chamber (e.g., the two arrowed lines in FIG. 27C with two center points), but where the exact center point is, and the furthest circle of said cross-section Whether the center point of the chamber line is the same as the center point of the nearest circular chamber line of said cross section (in Figures 27A-C, two center points were assumed) is known, considering the requirements. do not have. The chamber on the chamber wall is independent of the position of the actuator within the chamber and therefore independent of the internal pressure of the actuator.
SM-PVT2
A chamber (with the characteristics described above) moves in engagement and/or sealing over the spherical piston (FIG. 10H with the above-mentioned attempted configuration of the chamber) placed within the chamber. By moving the chamber above the piston, it can be driven around corners, similar to the front wheels of a vehicle. That is, both front wheels are not located at the same distance from the center of rotation, so in order to move the vehicle around corners, the wheels need to have independent axes, and the angle of the wheels with respect to said direction also depends on the direction of the wheels. The speeds of are also not the same at the same time. Therefore, the reaction force from the chamber on the contact area of the piston is not divided evenly over the circumference of said contact line, which circumference must be identical to said common boundary line (of the elongated chamber).

Therefore, in this case, engaging/sealingly connecting to the wall of the piston is not a circular line, but rather a circular part (on the boundary of the cross section closest to the center of the circular chamber) and a may be a combination of circular points between the circular portion (on the farthest boundary of the It may be between. This is not a major risk since the connection to the wall of the chamber only needs to be engaged in order to generate movement of the chamber. For circumferences of several sizes, the contact can range from a sealed state (closest to the center of the circular central axis of the chamber) to an engaged state (furthest from the center of the circular central axis of the chamber). , and occur between all types of sealed and engaged contact combinations.
This affects the magnitude of the friction between the piston and the chamber wall, and thus the direction in which relative motion occurs--in this hypothesized configuration, this direction should be in the direction of the chamber geometry. Yes -- this is the configuration we tried (Figures 27A-C).

To reduce friction, the spherical piston can rotate around a piston rod, the central axis of which can be parallel to an axis passing through the centre point of the chamber and perpendicular to the cross section of the chamber.
Actuator piston and chamber geometry The piston and piston-chamber configuration considers a conical tube with constant area, variable volume, flexible actuator, wall-contacting piston. Like a Fermi tube with a chamber in place. Explicit calculations of volume and contact area are added in a roughly commented Maple worksheet. Showing the actuator force distribution. Numbers are somewhat extreme.
--To explain the importance of geometry.
1. Fermi tube structure. The central base circle (around which the chamber is curved) is parameterized with unit velocity and has a radius of
The center of R and the origin (0,0,0) is a fixed (x, y, z) coordinate system. See the blue circles in Figures 32G, 32H, etc. The vector functions of the base circle are standard.

.
このベース円に沿って、ピストンがチャンバ壁と接触する回転角間隔u + [0, L] のみ
を考慮する。

.
Along this base circle, we only consider the rotational angular interval u + [0, L] in which the piston is in contact with the chamber wall.

In each orthogonal plane (see Figures 1 and 2), we define circles relative to the base circle of u*[0,L], ultimately tracing the entire chamber and the portion of the piston that has subsequent chamber wall contact. These circles have radius p(u), which depends on the base circle parameter u*[0,L], and each has its center on the base circle.

The family of circles describes the surface of a so-called Fermi tube around a base circle. We assume that the function p(u) is linear in u and the corresponding Fermi surface can be called a cone. See the corresponding

Cone effect (which ultimately drives it)
The piston in the chamber can be obtained by any other increasing function of u. The linear radius function is (which is applied to specific values of α and β in the Maple appendix and used for illustrations in this report):
2 Piston and chamber

次に、基準円のまわりに曲がっている半径関数p[u]を持つパラメータ化されたフェルミ管表面は、ベクトル関数によって与えられる。

Then the parametrized Fermi tube surface with radius function p[u] curved around the reference circle is given by a vector function.

ここで、e1(u)およびe2(u)は、図1に示すように、直交平面をベース円に貫通する直交単
位ベクトルである。

where e1(u) and e2(u) are orthogonal unit vectors that pass through the orthogonal plane to the base circle, as shown in FIG.

このとき、半径関数p(u)を持つパラメーター化されたフェルミ管ソリッドは、同様にベース円の周りで曲げられる。

Then the parametrized Fermi tube solid with radius function p(u) is similarly bent around the base circle.

.

表面はw = 1 = 1 を設定するだけで対応する固体から得られることに注意。

.

Note that the surface can be obtained from the corresponding solid simply by setting w = 1 = 1.

フェルミ管固体(回転角間隔[0, L]に相当)の体積は、次式により決定される。

The volume of a Fermi tube solid (corresponding to the rotation angle interval [0, L]) is determined by the following equation:

ここで、Jacobi関数積分は、次式の偏微分によって与えられる。

Here, the Jacobian integral is given by the partial derivative of

フェルミ管表面積(回転角間隔[0, L]に相当)は、次式により与えられる。

The Fermi tube surface area (corresponding to the rotation angle interval [0, L]) is given by

ここで、Jacobi関数のintegrandは次のようになります。

Now, the integrand of the Jacobian function is:

.

メープル出力付録は、考慮され示された特定の場合の幾何学を定義する定数の選択された値から計算されたそれぞれの総面積および総体積の計算例を含む。これは完全に一般的であり、幾何学的ディスクリプタ値の他の任意の選択で数値的に評価することができる。

.

The Maple Output Appendix contains examples of calculations of the respective total areas and volumes calculated from selected values of the constants that define the geometry of the particular case considered and shown, which are entirely general and can be evaluated numerically with any other choice of geometrical descriptor values.

Total area and total volume include the end cap values discussed here.

Piston and chamber 3

2. End Caps We assume that the end caps are spherical. This is not absolutely necessary. All that is needed is a circular fit to the tube parts of the chambers at both ends, and a handle on the sealed volume and total surface area of the piston. Both are most easily obtained. Considering the current model, with spherical end caps, see figures 32D and 32E. In fact, the spermatological assumption is not even completely realistic.

Given a perfectly elastic piston material, it will always have a constant mean curvature, even in the absence of wall contact. That is, in this situation the piston material (tends to) have identical spherical radii at both ends. This condition is not implemented in the current discussion. By describing the flexible piston material physically accurately, it is possible to estimate the actual shape of the end caps, the volume they enclose, and the internal pressure within the piston at each point in time. A spherical cap gives a simple geometrical representation of the area and the "enclosed" volume, i.e., the volume that is cut out of a solid sphere when the cap is separated by a plane cut. Therefore, we will continue with this Ansatz for spherical caps here.
The area of a cap with height h and base radius a is as follows (see Figure 3).

.
高さh、底面半径αのキャップの容積は、以下の通りである。

.
The volume of the cap with height h and bottom radius α is as follows.

.
完全性のために、u = 0とu = Lのそれぞれについて、それぞれのエンドキャップが取られる仮想球の半径も表示する。

.
For completeness, we also display, for each of u = 0 and u = L, the radius of the virtual sphere where the respective end caps are taken.

チューブの幾何学では、oとhの値は、それぞれuの末端値u = 0とu = Lで半径関数p(u)と
その導関数p'(u)だけで決まり、基底円の半径は何の役割も果たさない!

In tube geometry, the values of o and h are determined solely by the radius function p(u) and its derivative p'(u) at the extreme values of u, u = 0 and u = L respectively; the radius of the base circle plays no role!

したがって、球面Ansatzが4ピストンおよびチャンバーと仮定される場合、エンドキャ
ップ面積および体積は、pおよびp'のそれぞれの値によってのみ決定される。

Therefore, if the spherical Ansatz is assumed to be four pistons and chambers, the end cap areas and volumes are determined solely by the respective values of p and p'.

Since the end cap is supported or attached to the shaft, e.g. a rigid version of the base circle, this attachment and the induced coupling of forces there between the shaft and the piston changes the spherical shape of the piston end. let Given an accurate description of the mounting and piston material, it is possible to estimate the resulting deformed end cap geometry. This is not considered here.
3. Piston and Shaft Attachment Movement Most important is the exact area and geometry of the contact between the piston and the chamber wall. This contact activates the driving force on the piston. In this model, the wall contact is modeled as a Fermi tube around a given base circle, and the volume (pressure) and area (force on the wall) are calculated accordingly.

The actual sliding force along the chamber wall is obtained by a geometrically symmetric double projection (around its direction) of the total force in grey on the chamber segment shown in the figure.
The resulting sliding force is therefore proportional to the longitudinal length of the segment and the internal pressure of the piston: pressure = force per area.

Depending on the friction model (friction between the chamber wall and the piston) and the material properties of the piston (elasticity, etc.), the resulting force drives the segments in the longitudinal direction. Since the force on each segment is proportional to the longitudinal length of the segment and therefore to the distance of the segment from the center of the base circle, we can express the resulting motion of the free piston surface as a rotation about the center of the base circle (
The properties of the ionic liquid tend to be regulated (to the first order and very largely dependent on the physical descriptors exemplified above).

If the piston is attached to a shaft along a base circle in the chamber, the described force will similarly be applied to pull or push the attached circular shaft into a circular motion about the center of the base circle. It can be done.
19640 SUMMARY OF THE INVENTION European patent application 1179140B1 shows in Figures 5A-5H (inches) a piston (Figures 105A-105H of this patent application) fixed to a piston rod 45 for rotation about an axis 44. It includes six supporting means 43. The other end of said support means is assembled on an impermeable flexible sheet disposed between flexible O-rings, the flexible O-rings being hermetically connected to the walls of the piston-chamber combination. and the chamber is conical. The O-ring is squeezed against the wall by the support means due to a tension spring assembled on the piston rod on one side and on the support means near the O-ring on the other side, and the support means It spreads from the piston rod to the chamber wall. Further, a helical spring arranged in a circle on an impermeable sheet and having its center on the central axis of the chamber and pressing the O-ring against the wall of the chamber, the support means compressing the O-ring. Something you don't directly support. This was the main solution as the principle of the solution.

An unsolved aspect of this structure is that this impermeable flexible sheet is freely suspended and can be forced inward (in a deformed shape) by a piston (FIGS. 5G, 5H) when pressurized by a fluid below it. Another aspect that has not yet been fully developed is the proper assembly of the O-ring to the support means and to a means for holding the O-ring in place between the O-ring and the assembly point of the support means.

There can be two preferred solutions to avoid changes in the shape of the impermeable flexible sheet. Other solutions are possible but not shown.
One is that the impermeable flexible sheet can be assembled to the end of the piston rod, for example by a screw. Another solution is simply to vulcanize the sheet over and around the piston rod. Fixing the seat to the piston rod can substantially reduce (but avoid botting) changes in the shape of the seat when pressurized. Furthermore, the shape change of the sheet may be additionally reduced by appropriate reinforcement of the sheet. First, the sheet may need to have a production size with a circumference approximately equal to that of the chamber wall at the second longitudinal position. first when moving a piston from said second longitudinal position to a first longitudinal position while the piston is moving to a second longitudinal position in order to seal said sheet to the wall of the chamber; In the first case, it is necessary to spread the sheet. A tension spring on the support means can pull slightly more than the tension in the impermeable sheet to return it to its production size when the piston is not in the second longitudinal position. The third force is pulling the O-ring away from the wall, and this force occurs when the sheet bends upwards when pressurized. To substantially prevent this, the reinforcing bars may be made of flexible material in length or, as a spiral, made of non-flexible material, in the center of the piston rod. Concentric reinforcing bars may be provided that may be centered on the shaft. Other reinforcing bars are possible but not shown. The use of the reinforcing pattern means that the sheet can extend in 2D, in cross-section, perpendicular to and slightly in the direction of the central axis of the chamber.

Preferably, the reinforcing layer of the sheet is positioned closest to the high pressure side of the sheet, and a further unreinforced layer may be vulcanized on the first layer. The manufacturing thickness of each layer can be very thick so that the reduced thickness at the first longitudinal position may be sufficient in the longitudinal direction during proper operation of said piston.

Additionally, the O-ring can have a production size in which its outer circumference is approximately the size of the outer circumference of said chamber at the second longitudinal position.
Also, the manufacturing diameter of the O-ring should be large enough to compensate for the reduction in thickness when the piston is moved to the first longitudinal position.

An impermeable sheet may be vulcanized on/within the O-ring to achieve a proper seal if the O-ring is sealingly connected to the wall of the chamber.
A lying spring may be vulcanized to both the O-ring, the end of the support means, and the impermeable sheet. This brings the whole thing together.

When the water-impermeable flexible sheet is assembled on the piston rod, the spreading of said sheet can be caused substantially by the tension of the spring on said support means and the rotational force of said support means. The internal tension of the impermeable flexible sheet, the O-ring and the pushing force of the lying helical spring and the pushing force of said support means as well as the reaction force of the wall against the O-ring can be balanced, so that the O-ring is always pressed against the wall of the chamber to achieve a hermetically connected connection. The lying helical spring shown in the prior art drawings, which should mainly hold the O-ring in place between the ends of the support means, probably would not provide enough force to do the job. Instead, the use of an elastic metal rod would make it easier to hold the O-ring in place on the O-ring. The ends of said rod may slide between two adjacent support means, while the two rods may slide along each other through the support means.
19650 Summary of the invention European Patent No. 1 179 140 B1 discloses an elastically deformable means, which is reinforced by a rigid member and rotatably fixed to a common member, such as a piston rod, and a piston may be made of said elastically deformable means. The elastically deformable means may have a cross section of a cross section of a trapezius muscle. When moving in a chamber from a first longitudinal position to a second longitudinal position, the walls of said chamber in the second longitudinal position are parallel to the central axis of said chamber, and the trapezoid becomes more and more rectangular. The stiffening agent may rotate to an angle where the stiffening agent is approximately parallel to said central axis when the piston is moving from the first longitudinal position to the second longitudinal position.

The foam can expand from a second longitudinal position in the elongated chamber to a larger shape in the first longitudinal position. However, this can be done in a different way from expanding an inflatable container with a flexible wall having a manufacturing size, so that the circumference of the wall of the chamber in the second longitudinal position is approximately the same (see, for example, EP 1 384 004 B1). When it is moved to the first longitudinal position and needs to engage and connect with the wall of the chamber, the thickness of the wales of the container can be reduced ("balloon effect").

a motor having a pump with a piston engageably and/or sealably movable within a chamber;
- In an elastically deformable way, it is made of polyurethane foam.
- PU-foam includes polyurethane memory foam and polyurethane foam.
- Polyurethane foam consists mainly of polyurethane memory foam and a small amount of polyurethane foam.

The elastically deformable means may be made of a foam. For example, polyurethane foam may have particularly good properties for harsh environments, such as a moving piston in a pump chamber.

The growth in size of the foam when moving from the second longitudinal position to the first longitudinal position can be done by a fluid being placed, expanding the cells that may be present in said chamber. This occurs when the cells are open, i.e. the interior of said cells may be in communication with the atmosphere surrounding said bubbles in said chamber. The foam in the second longitudinal position therefore needs to be pressurized so that it can reduce the size of the open cells in the foam, and in the second longitudinal position it needs to be pressurized so that it can expand itself when moving to the first longitudinal position. The foam, and therefore the material of the walls of the open cells, can be very elastic, more than necessary. Such a material can be polyurethane foam ("PU" for short), a very flexible type of PU foam can be the so-called memory foam.

However, very flexible materials are not by themselves strong enough to withstand very large pressures, such as those required by pistons. To obtain better pressure resistance, a kind of sandwich can be made, which can be made, for example, from two layers of PU, one layer made of a less flexible PU foam than the PU memory foam, and a layer of PU memory foam, where the two layers can be glued together. If there is no interlayer space and/or it is difficult to produce a sandwich, a mixture of PU foam and PU memory foam can be the solution. A percentage of regular PU foam can be part of the total mixture.

In a motor in which the pump has the piston, a support member is bendable, the support member has a predetermined bending force, the member is locked in a holder connected to a piston rod and can rotate around the bent part of the stiffener in the holder. The end is subjected to pressure by an adjustable member, and the long end of the stiffener has an increased thickness.

The memory foam material will instantly return to its original size when depressed and released at normal operating temperatures, such as 10°-100° C. At lower temperatures, such as near freezing, it will take longer to respond to the demands of engaging and/or sealingly connecting to the walls of the chamber.
It may be too long. The stiffener needs to be made of a spring material so that it can press the foam outwards when the piston moves from the second longitudinal position to the first longitudinal position. The predetermined bending force may be whatever is needed and may for example be provided by the end of the stiffener, which is bent at a length much shorter than the entire length of the stiffener, thereby allowing an angle to lock the end of the stiffener in the holder. The predetermined bending force may be provided by an adjustable member pressing on the short end of the stiffener, i.e. it may be a rotatable member that can be locked in a certain position.

When moving from the first longitudinal position to the second longitudinal position, the foam may be pressed inwards by the walls of the chamber, and the foam must be in such a shape that there are no lateral forces, causing the casting foam to adhere to the hardener (preferably made of polyurethane) and lose its functionality.

In order to avoid that the stiffener is being inserted, another measure is to reduce the thickness of the long end of the stiffener to be close to where the pressure is obtained from the fluid below the piston in the chamber. By the way, increase it.

In a motor in which the pump has the piston,
- the flexible impermeable layer has a stress-free manufacturing size with a circumference approximately the same as the circumference of the wall of the chamber in the second longitudinal position. A foam piston with open cells is reliably connected to the wall of the chamber. In order to be able to be sealably connected to the chamber wall, an impermeable layer such as a natural rubber type must be added. This must fit a circumference of approximately the same dimensions as the expandable container type piston. It is therefore possible to require a size of said layer with the size of the circumference of the chamber wall in the second longitudinal position, which is stress-free and therefore requires that the assembly is around the foam under pressure. When moving from the second longitudinal position to the first longitudinal position, the foam and said stiffeners must press the layer into the shape of the foam (trapezoidal) when positioned in the first longitudinal position. When returning to the second longitudinal position, the layer can contract to the approximately rectangular shape of the foam in the second longitudinal position. The impermeable layer prevents communication ("exhalation") when the open cells move from the second longitudinal position to the first longitudinal position, and vice versa.
To be able to do this it may be necessary to be able to communicate with the fluid on the non-pressure side of said piston.
19650-1 Improved suspension of foam pistons, e.g. for pump purposes
WO2000/070227 discloses a foam piston which has the problem that the foam cannot be properly attached to the piston rod, especially during the return stroke. The reason is that the PU foam cannot be sufficiently fixed to the steel of the piston rod. Another difficulty is the release of the ready piston from the formwork due to the fact that the angle of the several rows of reinforcing pins increases from the piston rod side towards the outside. Even more difficult is that the PU foam is not sufficiently fixed to the metal reinforcing pins and the aforementioned surface is also rough. The improved suspension of the foam piston is the subject of this section of the patent application.

The piston disclosed in article 19650 of this patent application is very robust for professional use. For example, a less robust but still reliable construction may be required for use in a bicycle pump, where repairs may also be simple and straightforward.

Its solution follows the characterizing part of the independent claim. The use of metal pins can be used, for example, if the pin has received a surface coating of a suitable material, e.g. if the foam of the piston is also made of PU, before the foam piston is molded around said pin. To avoid peeling off the foam of the piston, the use of metal pins can be maintained without the pins being sufficiently fixed to the foam. The metal pin may be made of a steel type that can be magnetized. If the holder plate is magnetized so that the pin is designed to transmit compressive force from the high pressure side of the piston to the piston rod, said pin has a depth approximately relative to said surface of approximately the size of the diameter of said pin. It may also be fixed in a small hole in the hole. The hole may have a geometric design so that the pin can rotate within the hole. The pins are fixed to the holder plate as soon as they are close enough to each other so that a magnetic force acts. The holder plate may have a small thickness and may be glued directly or indirectly to the piston rod, on which the holder is assembled.

Yet another improved version of the pins is that they are made, for example, by injection molding of PU-plastic, which completely adheres to the same type of foam (eg PU foam) of the piston. Here, there is a further possibility to avoid peeling the PU foam from the pins by reducing the diameter of said pins by a large amount. Suspending a pin can be done as follows: The pin has a spherical end, which can be pressed smoothly into a holder plate having a spherical cavity, so that the spherical end rotates within the spherical cavity. be able to. The pin may have a certain preload so that the foam expands as the piston is moving from 2 inches to the first longitudinal position of the chamber, especially at lower temperatures. This can be done by providing the spherical end of the pin with a small lever arm, which is fixed in a plate of flexible material, such as rubber. This manufacturing angle is greater than the widest angle of the piston when it is in the first longitudinal position of the chamber.
19660 Summary of the invention
EP 1 179140 B1 designates an inflatable container piston type, EP 1 384 004 B1 indicates that this piston type has a stress-free manufacturing size and that its circumference in the second longitudinal position of the elongated chamber is similar to that of the first. In order to avoid the piston being obstructed when moving from a longitudinal position to a second longitudinal position, it is shown to have approximately the same circumference as one of the chambers.

The piston is expanding when it moves from the second longitudinal position to the first longitudinal position. According to European Patent No. 1 384 004 B1, the reinforcement for such a desired behavior may be a layer in which reinforcing strings are arranged parallel to each other in a non-stressed production model, these strings on the one hand is mounted on the piston rod, and the other connects the two slidable ends of the piston rod, and the rubber is vulcanized directly to both ends. The reinforcing layer is the inner layer, while another layer thicker than the layer with reinforcing strings protects said reinforcing layer. Both layers are vulcanized together and at the ends there may be another additional layer on top of both layers. The function of the second layer is furthermore to avoid that the reinforcing strings "protrude" from the outer layer, so that it is not possible to make sealing contact with the walls of the chamber. However, in the case of mating contact, this is just fine. The provision of a second layer on top of the reinforcing layer has worked well in practice, for example in a pump chamber (see 19620) where the force on the piston rod is constant. position) to φ59 mm (first longitudinal position), it has been shown that it is possible to expand around 330%. The angle at which the two reinforcing layers overlap each other is very small, and although the "second" layer mentioned above makes the container stronger, the expansion potential is much less than 330%.

The rubber layers may be of different types of rubber, but they must be compatible with each other so that they will vulcanize together and not deteriorate under normal operating conditions.
However, it has been observed that if an ellipsoidal vessel-type piston were to expand completely to a sphere, it would be highly likely to fracture. Therefore, the design can be modified to increase the length of the piston without changing other variables such as the chamber design. Thus, it never reaches the shape of a sphere, nor does it expand to 330%. It is only the ellipsoid that is approximately in the shape of a sphere. This makes the piston reliable even with one layer of reinforcement.

Also, the shape of the container in unstressed manufacturing conditions is such that the walls of the chamber at the second longitudinal position are parallel to the central axis, rather than the walls of the container being parallel to the central axis. That's possible. Only the walls of the chamber are free from the walls of the container in the stress-free manufacturing condition.
19660-1.2 Actuator Piston Operation Update The actuator piston includes a container, the container includes a wall surrounding a cavity, the cavity being expandable by a fluid, pressurizable, and/or foam. wherein the container, when pressurized, is arranged in a second longitudinal direction of the chamber in a chamber having different cross-sectional areas and different circumferential lengths at the first and second longitudinal positions. position to a first longitudinal position and having an at least substantially continuously different cross-sectional area and circumferential length at an intermediate longitudinal position between the first and second longitudinal positions; The cross-sectional area and circumferential length at the second longitudinal position are such that the cross-sectional area and circumferential length at the first longitudinal position are such that the actuator piston has a cross-sectional area and a circumferential length due to sliding of the container wall of the actuator piston on the chamber wall. said cross-sectional area and circumferential length at one longitudinal position.

This may also be the case for a chamber with different cross-sectional areas and cross-sections of equal circumferential length in the first and second longitudinal positions and in the intermediate longitudinal position.
Said wall of the piston may preferably have a symmetrical shape in the longitudinal direction of the chamber between the end cabs (movable and non-movable) about a transverse central axis, each symmetrical half having a , at least substantially continuously different cross-sectional areas, different longitudinal cross-sections at intermediate longitudinal positions between the transverse central axis and the end cab, and different circumferential lengths. This also applies when the circumferential lengths are equal.

Having a reinforcing layer on the wall of the actuator piston container makes the outside of the wall smooth and preferably convex when pressurized from within the cavity of the container. This provides a small contact area with the wall of the chamber. The expansion force of the wall of the container is directed perpendicular to the surface of the wall of the chamber. Depending on the ratio t/R (R=transverse radius of the longitudinal section, t=wall thickness of the actuator piston), the expansion force can be much greater than the pressure in the cavity of the actuator piston, especially when t/R<<<<.

If the actuator piston is disposed on a wall of the chamber that has a positive angle with the central axis of the chamber in a first longitudinal direction from a second longitudinal position, the first longitudinal position of the contact area closest to the first longitudinal position of the chamber (wall chamber-container)
Since there is no reaction force at the first longitudinal position of the upper chamber, the walls of the container at these positions will bend towards the walls of the chamber until the reaction force of the walls is equal to the expansion force of the walls of the container, resulting in an asymmetry in the reaction force from the walls of the chamber, and the walls of the corners of the actuator piston roll over the walls of the chamber. This rolling increases the contact height of the contact area of the walls of the container and the walls of the chamber, where the friction force increases. The expansion of the walls of the container of the actuator piston causes a small pressure drop in the walls of the container when the volume of the closed space is constant, which reduces the expansion force of the walls of the piston and also reduces the friction force. The actuator piston may move (slide) towards the first longitudinal position. This can reduce the contact height, since the part of the walls of the container closest to the second longitudinal position can reduce its circumference, and therefore the circumference of the contact area closest to the second longitudinal position can also reduce.

Due to the lubrication between the walls of the chamber and the walls of the container, the driving force is still greater than the frictional force and the actuator piston moves until the force asymmetry occurs again and the cycle starts again. Slide to a new chamber position closer to the first longitudinal position.

The main reason for the actuator piston's behaviour is to increase (=roll) the contact height in the longitudinal cross section of the engagement wall of the container and the wall of the chamber, thereby increasing the height in immediate succession of the existing height. The means for doing so may be, for example, an elliptical actuator piston.

If there is a bendable reinforcing layer in which the direction of the reinforcing bars is longitudinal approximately parallel to the central axis of the chamber, there are few transverse reinforcing bars, preferably symmetrical walls around the transverse axis of symmetry of the vessel. , the wall of the actuator piston preferably has a continuously smooth surface at least up to the vicinity of the contact area with the chamber wall. The wall of the container bends between the wall of the chamber and the wall of the container from the extreme periphery of the contact area closest to the first longitudinal position, allowing internal pressure to reach the wall of the chamber and thereby increase the contact surface area. receive. When the wall of the container approaches the second longitudinal position, the bend is then withdrawn from the wall of the chamber. Afterwards, the contact area between the walls of the container and the walls of the chamber is decreasing again.

The actuator piston deactivates towards the first longitudinal position if there is insufficient internal pressure to push the vessel wall of the actuator piston towards the chamber wall and circumferential leakage occurs. This can occur, for example, in the case of the chamber shown in section 19620 of this patent application, where there is a common boundary of 1 bar overpressure within the chamber. This is the first half of the explanation disclosed as "hesitating behavior."

In practice, it can be seen that when the pressure in the actuator piston cavity is very low, the receptacle of the actuator piston, whose movable carb is located closest to the first longitudinal position, moves in a step manner.

This is believed to be because, when the actuator piston moves from the second longitudinal position to the first longitudinal position, in addition to the expansion of the container wall due to internal pressure, the contact area of the actuator piston wall is increased and forced against the wall of the chamber closest to the first longitudinal position, increasing the frictional force.

The non-movable cab is in the position closest to the first vertical position and therefore "advances" the container in the direction of movement.
If the pressure is low, the movement will be smooth. The reason may be that the extra force of expansion of the container wall may add to the reduction of the expansion force so as not to exceed the frictional force.

The wall of the piston is thus made of a flexible reinforcing material that is pressurized through the enclosed space by a pressure source to smooth the outer surface of the piston wall, thereby providing a height of contact area between said piston wall and the wall of the chamber in the circumferential direction in the longitudinal cross section of the piston, said height varying in size during the movement of the piston at intermediate longitudinal positions between the second longitudinal position and the first longitudinal position.

This sliding can take place over several different contact areas of the actuator piston wall with the chamber wall, since the container wall is convex and flexible, while the different areas are arranged successively with each other.
19660-2 Expansion piston (strength and rigidity)
An expandable piston of the type in which the ellipsoid in the second longitudinal position of the chamber is becoming an enlarged ellipsoid/(approximately) sphere can be compared in terms of strength and rigidity to a thin-walled cylindrical container subjected to internal pressure.

The hoop stress σH expands the wall of the cylinder. The magnitude of said hoop stress σH1 is generally about 10 times the magnitude of the internal pressure in said cylinder. This is why the actuator piston, already at low internal pressure, moves from the second longitudinal position in the cylinder according to section 19620 of this patent application to the first longitudinal position.

The magnitude of the hoop stress σ depends on the longitudinal position of the piston, the size of the chamber and the number of reinforcement layers (for one reinforcement layer), and a.
- 2nd vertical position/φ17mm: Approximately 3 times the piston internal pressure
- 1st longitudinal position / φ 58 mm: approximately 3,8 times the piston internal pressure The type of expandable piston, in which the sphere in the second longitudinal position of the chamber is becoming an enlarged sphere, has a small thickness subject to internal pressure, in terms of strength and rigidity can be compared to a spherical container.

The applied spherical stress os3 can be compared to the cylindrical longitudinal stress σL which is half the hoop stress σH. This means that a spherical piston in a circular chamber could provide half of the ellipsoid's propulsion force. Therefore, multiple spherical pistons can be utilized within a circular chamber to reduce the size of the motor while having comparable torque.

Therefore, the stress that expands the wall of the actuator piston depends on the thickness t of the actuator piston wall and the transverse radius R of the actuator piston, Cx = [1-t/R] x the pressure in the actuator piston. Since R depends on the transverse radius of the chamber, Cx can differ from one longitudinal piercing of the actuator piston to another.
This may save energy, the amount depending on the slope of the wall.

The thrust of the actuator piston is the expansion force of the actuator wall times the sin of the angle between the wall of the chamber and the central longitudinal axis of the chamber. The larger the angle, the greater the propulsive force. For example, instead of the Golf MK II's gasoline motor, you can find a motor that has a φ81mm cylinder with a stroke length of 77.4mm and operates between 9-10 Bar.

The inclination of the chamber is a = 10°, sin 10° = 0,174, cylinder φ = 81mm is kept in the first vertical position, φ53,7mm in the second vertical position, pressure 3.5mm at 2nd LP = 10 Bar, 1st LP = 2,25 Bar.
(Conclusion)
It is possible to use a motor according to the invention, which is close to the size of current gasoline motors.
19680-2- Pump piston consisting of a container The purpose of this section is to develop a container-type piston that can be used in pumps, using the principles disclosed in WO2002/077457, and here we will discuss the The perimeter has a production size comparable to the production size of the perimeter of the second longitudinal position. That is, the inflatable container piston will be inflated from the second vertical position in order to move to the first vertical position and return rearwardly without obstruction. However, the piston has a contact portion between a continuous outer wall of the piston and a wall of the chamber located below the transverse axis of the piston, and a movable cab closest to the first longitudinal position; It has been experienced that the movement from the second vertical position to the first vertical position by rolling, sliding, rolling, etc. is carried out only by the internal pressure of said piston with the movable cab closest to the position.

Experience has shown that if the walls of the chamber are parallel to the central axis of the chamber, the self-propelling capability will fail. Therefore, to use a piston in a pump, one must avoid "rolling" the walls of the piston over the walls of the chamber. This can be done by discontinuing the outer walls of the piston.

Creating a self-propelled actuator piston, i.e. a "rolling-slide-rolling" in which the wall of the piston covers the wall of the conical chamber, should be avoided as it generates a driving force in the opposite direction of the pumping force. To do so, the contact area between the walls of the chamber and the wall of the piston is limited to a certain area of the wall of the piston ("disk continuous"), which can be done in at least two ways.

The contact area may be a separate part of the piston wall and may be larger than the remaining part of the piston wall, the part of the piston closest to the second longitudinal position being It can have a smaller cross-sectional circumference than that of the contact area. The hoop stress in the wall of the inflatable container piston (see sections 19660, 207 and 653 of this patent application) causes an expansion of the circumference of said wall, and the source of the actuator piston is the internal overpressure. It becomes self-propelled.

The hoop therefore states that it is the ability to jam, as well as to have a large impact on the sealing ability of the piston to the chamber wall when the piston is pushed from a first vertical position to a second vertical position. For a given R/t ratio (large radius compared to a small wall thickness (layer with reinforcement layer)), the hoop stress is much larger than the internal pressure. The first idea is that the pressure of the gas medium in the piston is related to the pressure of the medium in the chamber where the piston is located and is compressed by the piston "thus". However, the piston must seal at any pressure of the medium being pumped.

At the same time, in the chamber shown in section 19597 of this patent application, it has been shown that it is impossible to manually push the expanded piston (using a compressible medium such as nitrogen), and the piston from a first longitudinal position to a second longitudinal position, comprising a compressible medium having a 1 to 1 1/2 bar (absolute) overpressure (atmospheric pressure) at the first longitudinal position. The medium for expanding the wall of the piston may preferably be as follows.

Unlike a compressible medium such as a gas, for example a foam may contain a fluid in its pores, and the foam preferably has an open structure, said foam preferably being at atmospheric pressure in the first longitudinal position, and optionally at a low overpressure (e.g. 1
It is preferred that the foam, preferably the medium does not expand the wall of the piston, and optionally there may be a combination of the two factors, such as a non-compressible medium (e.g. a liquid such as water) different from a compressible medium.

and communicating with an enclosed space, such as a hollow piston rod, the hollow piston rod being in communication with a closed space, such as a hollow piston rod, the hollow piston rod being in communication with a closed space, such as a hollow piston rod, the hollow piston rod being in communication with a closed space, such as a hollow piston rod, wherein the hollow piston rod is in communication with a closed space, such as a hollow piston rod, the hollow piston rod comprising , when the foam is compressed by the walls of the piston, when the piston moves from a first longitudinal position to a second longitudinal position, the enclosed space (
For example, WO2010/094317 or ).

Sections 207 and/or 653) are in order to avoid sudden increases in internal pressure and thereby avoid possible disturbances.
An alternative solution to avoid the creation of self-propelled actuator pistons is that when using an inflatable piston, the piston may have walls without reinforced parts, thereby Reinforcement may be minimal, only to avoid excessive swallowing of the walls of the piston when inflated, and is foam, preferably open cell foam. The open cell can contain a fluid, preferably a gaseous medium, optionally a liquid, or a combination of liquid and gaseous medium. The foam may be inserted into the piston when the piston is in its first longitudinal position and the walls of the piston are engaged and/or sealingly connected to the walls of the chamber, so that , when the wall of the piston is under tension, it fills the maximum volume of the piston and has a smaller wall thickness than when manufactured (in the second longitudinal position). The foam is compressible to a higher order (e.g. 5:1 when using section 19660 and/or 19680 pistons) so that when in the second longitudinal position the piston Can be filled with dense foam. In this case, almost all of the open cells are closed. When moving from a first longitudinal position to a second longitudinal position, the medium within the foam can then be removed from the piston, for example onto a piston rod. In order to avoid high pressure building up in said piston rod, the piston rod can have a movable piston that reduces the volume of the medium in the open cell (if not in the second longitudinal position). This high pressure causes jamming when the piston becomes the actuator piston and moves from the first longitudinal position to the second longitudinal position. The result may be a piston that is changing size (and may even change shape) during the pump stroke.
It may only provide sufficient sealing force to the walls of the chamber without moving itself and without disturbing the walls of the piston, which are made of a flexible material such as rubber, for example. To make the piston a reliable piston for the pump.

The manufacture of the container piston comprising foam is as follows, the wall of the container piston being manufactured when it is in the second longitudinal position. Fluid is then injected into the cavity of the container when in the first vertical position. That is, the mobile cab moves towards the other cab and the walls of the container curve. The position of the movable cap is then fixed and fluid is then released from the cavity. Now inject the foam blend and close the continer cavity. After curing, remove the movable cap fixture. Contraction of the walls of the container may then occur due to the nature of the foam containing open cells. This shrinkage is compensated for by negligibly increasing the pressure of the medium in the open cell or by having another cavity in an impermeable flexible wall placed in the center of the foam. The cavity may be inflated and the foam then pressed against the wall of the container piston to bring the wall into its originally planned position.

The separate wall of the piston "protrudes" from the wall of the piston, i.e. it has a larger circumference than the rest of the wall of the piston is close to, while the wall of the piston has a larger circumference than the wall of the piston that is separate from the wall of the piston. The circumferential transition of is more or less abrupt or step-like.

The contact area of the separate part with the wall of the chamber may be small, which may be done by selecting the shape of the right side of the separate part, for example a circular segment, the top of which is in contact with the wall of the chamber.
207 SUMMARY OF THE INVETION In general, a new design, for example for a chamber and piston combination for a pump, must ensure that the force applied to operate the pump during the entire period of pump operation is low enough that the user feels comfortable, that the stroke length is suitable, especially for women and teenagers, that the pump operation time is not long, and that the pump has a minimum of components that are reliable and requires little maintenance time.

In a first aspect, the present invention relates to a piston and a chamber combination, the chamber comprising:
The chamber defines an elongated chamber having a longitudinal axis, the chamber having at a first longitudinal position:
The piston has a first cross-sectional area and, at a second longitudinal position thereof, a second cross-sectional area, the second cross-sectional area being no greater than 95% of the first cross-sectional area, and the change in cross-sectional area of the chamber is at least substantially continuous between the first longitudinal position and the second longitudinal position. The piston is adapted to accommodate the cross-section of the chamber as it moves from the first longitudinal position of the chamber to the second longitudinal position.

In this context, the cross section is preferably taken perpendicular to the longitudinal axis.
Also, the change in the cross-section of the chamber is preferably such that the piston can seal against the inner wall of the chamber during movement between the first and second longitudinal positions. , at least substantially continuous, ie without abrupt changes in the longitudinal section of the inner wall.

In the present context, the cross-sectional area of a chamber is the cross-sectional area of the interior space of the chamber at a selected cross section.
Thus, as will become apparent below, varying the area of the interior chambers actually allows the combination to be tailored to multiple situations.

In a preferred embodiment, this combination is used as a pump, whereby the movement of the piston compresses air, which is output through the valve, for example to a tire. The area of the piston and the pressure on the other side of the valve determine the force required to provide air flow through the valve. Thus, an adaptation of the required force can occur. The amount of air delivered also depends on the area of the piston. However, to compress the air, first the movement of the piston is relatively easy (the pressure is relatively low) and this can be done with a large area. Overall, therefore, a larger amount of air can be delivered at a given pressure during one stroke of a certain length.

Of course, the actual reduction in area will depend on the forces in question as well as the intended use of the combination.
Preferably, the second cross-sectional area is 95-15%, such as 95-70% of the first cross-sectional area. In certain circumstances, the second cross-sectional area is about 50% of the first cross-sectional area.

Many different techniques can be used to achieve this combination, which are further described in relation to subsequent aspects of the invention.
In one such technique, a piston comprises a plurality of at least substantially rigid support members rotatably fixed to a common member and elastically deformable means carried by the support members for sealing against an inner wall of the chamber, the support members being rotatable between 10° and 40° relative to a longitudinal axis.

In this situation, the common member may be attached to the handle for use by an operator, and the support member extends within the chamber in a direction relatively remote from the handle. Preferably, the support member is rotatable at least substantially parallel to the longitudinal axis. Additionally, the combination may further include means for biasing the support member against the inner wall of the chamber.

Another technique is for the piston to include an elastically deformable container containing a deformable material. In such situations, the deformable material may be a fluid, or a mixture of fluids such as water, steam, and/or gas, or a foam.

Additionally, in a longitudinal cross section, the container may have a first shape in a first longitudinal direction and a second shape in a second longitudinal direction, the first shape being a second shape. different from.
Then, at least a portion of the deformable material may be compressible, and the first shape has a larger area than the area of the second shape. Alternatively, the deformable material may be at least substantially incompressible. The piston includes an enclosed space in communication with the deformable container, the enclosed space having a variable volume. This volume can be varied by the operator and can include a spring-loaded piston.

Yet another technique is one in which 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 vertical position and the second vertical position.

In that 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 it can be at least 70%, such as at least 80%, such as at least 90% larger than the second cross-sectional area.

Additionally, the first cross-sectional shape may be at least substantially circular, and the second cross-sectional shape may be elongated, such as an oval, and the first dimension may be at least substantially circular. It has at least two first dimensions that are at least three, preferably at least four times as large at an angle.

Further, the first cross-sectional shape may be at least substantially circular and the second cross-sectional shape comprises at least two or more at least substantially elongated, eg, lobe-shaped, parts.

Also, in a cross-section in the first longitudinal position, the first circumference of the chamber may be 80-120%, such as 85-115%, preferably 90-110, such as 95-105, preferably 98-102%, of the second circumference of the chamber in a cross-section in the second longitudinal position.
The circumference of the first circle and the second circle are at least substantially the same.

An optional or additional technique includes an elastically deformable material adapted to conform to a cross-section of the chamber as the piston moves from a first longitudinal position of the chamber to a second longitudinal position of the chamber, and a coiled flat spring having a central axis at least substantially along the longitudinal axis and disposed adjacent to the elastically deformable material to support the elastically deformable material in the longitudinal direction.

In such a situation, the piston is arranged between the elastically deformable material and the spring, and the support means is rotatable along the interface between the spring and the elastically deformable material. , a plurality of flat support means may further be provided.

The support means may be configured to rotate from a first position to a second position, and in the first position its outer boundary may be contained within the first cross-sectional area and the support means may be configured to rotate from a first position to a second position; In position 2, its outer boundary may be included within the second cross-sectional area.

In a second aspect, the invention relates to a combination of a piston and a chamber, the chamber defining an elongated chamber having a longitudinal axis, the chamber having a first cross-sectional area at a first longitudinal position thereof and a second cross-sectional area at a second longitudinal position thereof, the first cross-sectional area being greater than the second cross-sectional area, the change in cross-sectional area of the chamber being at least substantially continuous between the first and second longitudinal positions, the piston adapted to accommodate the cross-section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber, said piston comprising a plurality of at least substantially rigid support members rotatably fixed to a common member and elastically deformable means supported by the support members for sealing against an inner wall of the chamber, the support members being rotatable between 10° and 40° relative to the longitudinal axis. Preferably, the support members are rotatable at least substantially parallel to the longitudinal axis.

Thus, the way in which the piston can accommodate different areas and/or shapes is that it comprises a number of rotatably fixed means for carrying the sealing means. One preferred embodiment is where the piston has the general shape of an umbrella.

Preferably, the common member is attached to a handle for use by an operator, such as when the combination is used as a pump, and the support member extends within the chamber in a direction relatively away from the handle. This has the advantage that increasing pressure by forcing the handle into the chamber simply presses the support means and sealing means against the walls of the chamber, increasing the seal.

To ensure a seal after the stroke, the combination preferably includes means for biasing the support member against the inner wall of the chamber.
In a third aspect, the invention relates to a piston and chamber combination, the chamber defining an elongate chamber having a longitudinal axis, the chamber having a first cross-sectional area thereof in a first longitudinal position; at its second longitudinal position, the chamber has a second cross-sectional area, the first cross-sectional area being greater than the second cross-sectional area, and the change in cross-sectional area of the chamber differs between the first longitudinal position and the second cross-sectional area; at least substantially continuous between two longitudinal positions, the piston being adapted to accommodate the cross-section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber. It has become. The piston includes an elastically deformable container containing a deformable material.

Thus, by providing an elastically deformable container, changes in area and/or shape may be provided. Naturally, this container should be sufficiently fixed to the piston so that it follows the rest of the piston as it is moved within the chamber.

The deformable material may be a fluid or a mixture of fluids such as water, steam and/or gas, or foam. This material or parts of it may be compressible, such as a gas or a mixture of water and gas, or may be at least substantially incompressible.

If the cross-sectional area changes, the volume of the container may change. Thus, in longitudinal section, the container may have a first longitudinal shape and a second longitudinal shape, the first shape being different from the second shape. different. In one situation, at least a portion of the deformable material is compressible and the first shape has a larger area than the area of the second shape. In such situations, the overall volume of the container changes and the fluid must be compressible. Alternatively or optionally, the piston may include a second enclosed space in communication with the deformable container, the enclosed space having a variable volume. In this way, this enclosed space can take in fluid when the deformable container changes volume. The volume of the second container can be varied by the operator. In this way, the overall pressure or the maximum/minimum pressure of the container can be changed. Additionally, the second sealed space may include a spring biased piston.

Preferably, means are provided for defining the volume of the enclosed space such that the pressure of the fluid within the enclosed space is related to the pressure of the fluid between the piston and the second longitudinal position of the container. In this way, the pressure in the deformable container can be varied to obtain a proper seal.

A simple method would be to have the defining means configured to define the pressure in the enclosed space to be at least substantially the same as the pressure between the piston and the second.
Longitudinal position of the container In this situation, a simple piston can be provided between the two pressures (as it does not loosen any of the fluid in the deformable container).

In fact, this use of pistons allows any relationship between pressures to be defined in that the enclosed space through which the piston translates can taper in the same manner as the main chamber of the combination.

To withstand both friction and shape/dimensional changes against the chamber walls, the container can include an elastically deformable material that includes forcing means such as fiber forcing.
In order to achieve and maintain a proper seal between the container and the chamber wall, internal pressure, such as the pressure created by the fluid within the container, causes the piston to move from a first longitudinal position to a second longitudinal position. It is preferred that the pressure be higher than the maximum pressure of the surrounding atmosphere during the process, or vice versa.

In yet another aspect, the invention relates to a combination of a piston and a chamber, the chamber defining an elongated chamber having a longitudinal axis and having a first cross-sectional shape and area at a first longitudinal position thereof and a second cross-sectional shape and area at a second longitudinal position thereof, the first cross-sectional shape being different from the second cross-sectional shape, the change in cross-sectional shape of the chamber being at least substantially continuous between the first longitudinal position and the second longitudinal position, and the piston adapting to the cross-section of the chamber as it moves from the first longitudinal position to the second longitudinal position of the chamber.

This very interesting aspect is based, for example, on the fact that different shapes of geometric figures have different relationships between their circumference and their area. Also, the two shapes may be changed. such that the chamber can have one cross-sectional shape at one longitudinal position of the chamber and one cross-sectional shape at another longitudinal position while maintaining the preferred smooth transition of surfaces within the chamber. , can be performed continuously.

In this context, the cross-sectional shape is the overall shape, regardless of its size. Two circles have the same shape even though one has a different diameter than 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 50%, such as at least 60%, Preferably it is at least 70%, such as at least 80%, such as at least 90% larger than the second cross-sectional area.

In a preferred embodiment, the first cross-sectional shape is at least substantially circular, the second cross-sectional shape is elongate, such as an oval, and the first dimension is relative to the first dimension. It has at least two first dimensions that are at least three, preferably at least four times as large in angle.

In another preferred embodiment, the first cross-sectional shape is at least substantially circular and the second cross-sectional shape comprises at least two or more at least substantially elongated, eg lobe-shaped sections.

The first circumference of the chamber in the cross-section at the first longitudinal position is 80-120%, such as 85-115%, preferably 85-115% of the second circumference of the chamber in the second longitudinal cross-section. Some advantages are seen when it is between 90 and 110, such as between 95 and 105, preferably between 98 and 102%. When trying to seal against walls with varying dimensions, problems may arise due to the fact that the sealing material provides an adequate seal and its dimensions should be varied. The seal can be more easily controlled if the surroundings change only slightly, as is the case in the preferred embodiment. Preferably, the first and second circumferences are at least substantially the same, so that the sealing material is only curved and not stretched to a significant extent.

Alternatively, it may be desirable for the circumference to change slightly when the sealing material is bent or deformed, for example in that as it is bent, one side of it compresses and the other side stretches. Overall, it may be desirable to provide a desired shape that is at least close to the circumference that the sealing material automatically "selects."

One type of piston that may be used in this type of combination includes a plurality of at least substantially rigid support members rotatably fixed to a common member and supported by the support members for sealing to an inner wall of the chamber. and an elastically deformable means.

Another type of piston comprises an elastically deformable container containing a deformable material. Another aspect of the invention relates to a combination of a piston and a chamber, the chamber defining an elongated chamber having a longitudinal axis, the chamber having, at a first longitudinal position thereof:
a piston having a first cross-sectional area and, at a second longitudinal position thereof, a second cross-sectional area, the first cross-sectional area being greater than the second cross-sectional area, the change in cross-sectional area of the chamber being at least substantially continuous between the first longitudinal position and the second longitudinal position, the piston comprising: an elastically deformable material adapted to conform to the cross-section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber; and a coiled flat spring having a central axis at least substantially along the longitudinal axis and disposed adjacent to the elastically deformable material to support the elastically deformable material in the longitudinal direction.

This embodiment solves the potential problem of simply providing a large mass of elastic material as a piston. The fact that the material is elastic presents the problem of deformation of the piston and, if pressure is increased, motoring the lack of a seal due to the elasticity of the material. This is particularly problematic when the dimensional change required is large.

In this embodiment, the elastic material is supported by a helical flat spring. The helical spring can expand and compress to follow the area of the chamber, while the flat structure of the spring material ensures that the spring does not deform under pressure.

For example, to increase the engagement area between the spring and the deformable material, the piston may further comprise a number of flat support means disposed between the elastically deformable material and the spring, the support means being rotatable along the interface between the spring and the elastically deformable material.

Preferably, the support means is configured to rotate from a first position to a second position, in the first position its outer boundary may be contained within the first cross-sectional area; In position 2, its outer boundary may be contained within the second cross-sectional area.

Another aspect of the invention relates to a piston and chamber combination, the chamber defining an elongated chamber having a longitudinal axis, the piston movable within the chamber from a first longitudinal position to a second longitudinal position, the chamber having an inner wall elastically deformable along at least a portion of the inner chamber wall between the first longitudinal position and the second longitudinal position, the piston having a first cross-sectional area at the first longitudinal position when positioned at the piston and a second cross-sectional area at the second longitudinal position when positioned at the piston, the first cross-sectional area being greater than the second cross-sectional area, and the change in cross-section of the chamber being at least substantially continuous between the first longitudinal position and the second longitudinal position as the piston is moved between the first longitudinal position and the second longitudinal position.

Thus, alternatively to a combination where the piston adapts to changes in the cross section of the chamber, this aspect relates to a chamber having an adapting ability.
Of course, the piston may be made of an at least substantially incompressible material or a combination of a compliant chamber and a compliant piston, such as the piston according to the above embodiment.

Preferably, the piston has a shape in cross-section along the longitudinal axis that tapers towards the second longitudinal position.
A preferred method of providing a conforming chamber may include the chamber including an outer support structure surrounding an inner wall and a fluid retained by a space defined by the outer support structure and the inner wall. As such, the selection of fluids or combinations of fluids helps define chamber properties such as the seal between the wall and the piston, and the required force.

It is clear that depending on where the combination is found, one of the piston and the chamber may be stationary, the other moving, or both moving. This does not affect the function of the combination.

Naturally, the combination of the present invention can be used for many purposes, mainly focusing on the novel method of providing an additional way of adjusting the translation of the piston to the force required/to be taken. In fact, the cross-sectional area/shape can be varied along the length of the chamber to adapt the combination for a specific purpose and/or force. One purpose is to provide a pump for use by women and teenagers, which should still be able to exert a constant pressure. In such a situation, an ergonomically improved pump is required by determining the force a person can exert at any position of the piston, thereby providing the chamber with the appropriate cross-sectional area/shape.
Give shape.

Another use of this combination is for shock absorbers which would determine the range/shape that would be required for a particular shock (force) travel.Also, an actuator may be provided where the amount of fluid introduced into the chamber provides different travel of the piston depending on the actual position of the piston prior to introducing the fluid.

Indeed, the nature of the piston, the relative positions of the first and second longitudinal positions, and the arrangement of any valves connected to the chambers can provide pumps, motors, actuators, shock absorbers, etc. with different pressure characteristics and different force characteristics.

Where the piston pump is a hand pump for tire inflation purposes, it may have an integral connector in accordance with that disclosed in PCT/DK96/00055 (including the U.S. continuation of the April 18, 1997 part), PCT/DK97/00223 and/or PCT/DK98/00507. The connector may be equipped with any type of integral pressure gauge. For example, in a piston pump according to the invention used as a floor pump or "car pump" for inflation purposes, a pressure gauge arrangement may be incorporated into the pump.

For example, certain piston types, such as those in Figures 4A-F, 7A-E, 7J, 12A-C, can be combined with any type of chamber.
For example, certain mechanical pistons as shown in Figures 3A-C, certain compound pistons as shown in Figures 6D-F, and certain convex pistons as shown in Figure 7L, for example. A combination with a chamber having a circumferential length may be a good combination.

Compound piston combinations such as those shown in Figures 9-12 can be used successfully with convex chambers despite possible variations in circumference.
The "Enbrel-type" piston shown in this application has an open side on the side where the pressure of the medium in the chamber is loading the "Enbrel" on the open side. It is also very possible that the "Embrella" is working in the opposite direction.

As shown, an inflatable piston having a skin with a fibrous structure has an overpressure within the piston relative to the pressure within the chamber. However, it is also possible for the pressure in the piston to be equal to or less than the pressure in the chamber, so that the fiber is under pressure rather than under tension. The resulting shape may differ from that shown in the drawings. In that case, the load adjustment means must be adjusted differently and the fiber must be supported. Load adjustment means are shown, for example. 9D or 12B can then be arranged such that movement of the piston of the means exerts a suction force on the piston, for example by elongation of the piston rod, so that the piston is located on the opposite side of the bore of the piston rod. The change in the shape of the piston is not different and a collapse is obtained. The lifespan may be shortened.

These embodiments make it possible to obtain a reliable and inexpensive pump that is optimized for manual operation, such as a universal bicycle pump operated by women and teenagers. The shapes of the walls of the pressurizing chamber (longitudinal and/or cross-sectional) and/or piston means of the illustrated pumps are exemplary and can be varied depending on the design specifications of the pump. The invention also relates to, for example, multi-stage piston pumps and dual-function pumps, piston pumps driven by motors, such as pumps in which only the chamber or piston is moving, and types in which both chamber and piston are moving simultaneously. , can be used for all kinds of pumps. Piston pumps can pump any type of media. These pumps can be used for all kinds of applications, such as pneumatic and/or hydraulic applications. The present invention is also applicable to pumps that are not manually operated. This reduction in power means significantly less investment in equipment and significantly less energy in operation. The chamber can be manufactured, for example, by injection molding, such as from a tapered swage tube.

In a piston pump, the medium is sucked into a chamber, which is then closed by a valve arrangement. The medium is compressed by the movement of the chamber and/or the piston, and a valve can release this compressed medium from the chamber. In an actuator, the medium is forced into the chamber via a valve arrangement, which moves the piston and/or the chamber, initiating the movement of the attached device. In a shock absorber, the chamber may be completely closed, and the chamber can compress a compressible medium by the movement of the chamber and/or the piston. In the case of incompressible media, for example, the piston may be equipped with several small channels that provide dynamic friction to slow the movement.

Furthermore, the invention can also be used in propulsion applications where a medium can be used to move the piston and/or the chamber, and where a shaft can be rotated, for example like a motor. The above combinations are applicable to all the above applications.

The invention therefore also relates to a pump for pumping fluid, which pump comprises a combination according to any of the above embodiments, means for engaging the piston from a position external to the chamber, connected to the chamber and valve means. and a fluid outlet connected to the chamber. In certain situations, the engagement means may have an outer position with the piston in its first longitudinal position and an inner position with the piston in its second longitudinal position. This type of pump is preferred when pressurized fluid is desired.

In another situation, the engagement means may have an outer position with the piston in its second longitudinal position and an inner position with the piston in its first longitudinal position. This type of pump is preferred when no substantial pressure is desired, but simply to transport fluid.

In situations where the pump is configured to stand on the floor and the piston/engaging means are configured to force downward compression of fluid such as air, the maximum force is ergonomically /Engagement means/may be provided at the lowest position of the handle. Therefore, in the first situation this means that the highest pressure is applied there. In the second situation, this simply means that the largest area and therefore the largest volume is found at the lowest position. However, due to the fact that in order to open a tire valve, a pressure is required that exceeds the pressure inside the tire, for example, the resulting pressure opens the valve and the larger cross-sectional area forces the fluid into the tire. A minimum cross-sectional area just before the lowest position of the engagement means may be desired (see Figure 2B).

The present invention also relates to a shock absorber and means for engaging a combination according to any one of the aspects of the combination with a piston from a position outside the chamber, the engaging means being such that the piston is in its first position. and means having an outer position in which the piston is in a second longitudinal position and an inner position in which the piston is in a second longitudinal position, the absorber further comprising a fluid inlet connected to the chamber, and a valve can include means. The absorbent body may also include a fluid outlet connected to the chamber and may include valve means. Preferably, the chamber and the piston form an at least substantially sealed cavity containing a fluid, which fluid is compressed as the piston moves from the first longitudinal position to the second longitudinal position. Typically, the absorber includes means for biasing the piston towards the first longitudinal position.

Finally, the present invention relates to an actuator comprising a combination according to any of the aspects of the combination, means for engaging the piston from a position outside the chamber, and means for introducing fluid into the chamber to displace the piston between a first longitudinal position and a second longitudinal position, the actuator may comprise a fluid inlet connected to the chamber and comprising a valve means. A fluid outlet connected to the chamber and including a valve means may also be provided. Additionally, the actuator may comprise means for biasing the piston to the first or second longitudinal position.

The various embodiments described above are provided by way of example only and should not be construed as limiting the invention. Without departing from the true spirit and scope of the invention, those skilled in the art will appreciate the variety of elements that may be made into the invention without departing from the true spirit and scope of the invention. Modifications, changes and combinations will be readily recognized.

All types of pistons, especially containers with elastically deformable walls, may be sealingly connected to the chamber wall during movement between longitudinal positions, or may be engagedly connected to the chamber wall. Does not need to be connected. Alternatively, the connection may be made in a sealing manner by engaging the chamber wall. Additionally, there may be no engagement between any of the walls and the walls may contact each other. This occurs, for example, when the container is being moved from a first longitudinal position to a second longitudinal position within the chamber.

The type of connection between said walls (sealing and/or engagement and/or contact and/or no connection) is determined by the correct internal pressure within said vessel walls, i.e. high pressure for sealably connecting, low pressure for engaging , and can be achieved by using atmospheric pressure (for production-sized vessels) for no connection, and thus an enclosed space where the pressure inside the vessel can be controlled from a position outside the piston. Therefore, a container with a closed space is preferable.

Another option for an engaging connection is a thin wall of the container, which may have reinforcements protruding from the surface of said wall such that leakage can occur between the container wall and the chamber wall.
207 SPECIFICALLY PREFERRED EMBODIMENTS According to one embodiment of the present invention, there is provided a piston and chamber combination, the chamber defining an elongated chamber having a longitudinal axis, the chamber having a first cross-sectional area at a first longitudinal position thereof and a second cross-sectional area at a second longitudinal position thereof, the second cross-sectional area being no greater than 95% of the first cross-sectional area, the change in cross-sectional area of the chamber being at least substantially continuous between the first longitudinal position and the second longitudinal position, and the piston adapted to conform to the cross-section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber.

Preferably, the second cross-sectional area is between 95% and 15% of the first cross-sectional area.
Preferably, the second cross-sectional area is 95-70% of the first cross-sectional area.
Preferably, the second cross-sectional area is about 50% of the first cross-sectional area.

Preferably, the piston is a plurality of at least substantially rigid support members rotatably fixed to a common member for sealing against the inner wall of the chamber, the elastically deformable means being supported by the support members. The support member includes a plurality of support members rotatable between 10° and 40° with respect to the longitudinal axis.

According to one embodiment of the invention, there is also provided a combination in which the support member is rotatable at least substantially parallel to the longitudinal axis. Preferably, the common member is attached to a handle for use by an operator, and the support member extends within the chamber in a direction relatively away from the handle. Preferably, the combination further includes means for biasing the support over an inner wall of the chamber. Preferably, the piston comprises an elastically deformable container containing a deformable material. Preferably, the deformable material is a fluid or mixture of fluids, for example water, steam, and/or gas, or a foam.

Preferably, in a cross section through the longitudinal direction, the container has a first shape in the first longitudinal direction, a second shape in the second longitudinal direction, and the first shape has a second shape. different from. Preferably, at least a portion of the deformable material is compressible and the first shape has a larger area than the area of the second shape. Preferably the deformable material is at least substantially incompressible. Preferably, the piston includes a chamber communicating with the deformable container, the chamber having a variable volume. Preferably, the volume can be varied by the operator. Preferably, the chamber includes a spring-loaded piston. Preferably, the combination further includes means for defining the volume of the chamber such that the pressure of the fluid within the chamber is related to the pressure of the fluid between the piston and the second longitudinal position of the container. Preferably, the defining means are configured to define the pressure within the chamber to be at least substantially the same as the pressure between the piston and the second longitudinal position of the container. Preferably, the first cross-sectional shape is
Unlike the second cross-sectional shape, the change in cross-sectional shape of the chamber is at least substantially continuous between the first longitudinal position and the second longitudinal position. 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 50%, such as at least 60%, Preferably it is at least 70%, such as at least 80%, such as at least 90% larger than the second cross-sectional area.

Preferably, the first cross-sectional shape is at least substantially circular, the second cross-sectional shape is elongated, such as an oval, and the first dimension is at an angle to the first dimension. , at least twice the first dimension, which is at least three, preferably at least four times as large. Preferably, the first cross-sectional shape is at least substantially circular and the second cross-sectional shape includes at least two or more at least substantially elongated, eg lobe-shaped parts. Preferably, the first circumference of the chamber in cross-section at the first longitudinal position is between 80 and 120%, such as between 85 and 115%, of the second circumference of the chamber in cross-section at the second longitudinal position. , preferably 90-110, such as 95-105, preferably 98-102%. Preferably, the first and second circumferences are at least substantially the same. Preferably, the piston is at least substantially vertically disposed with an elastically deformable material adapted to accommodate the cross section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber. a coiled flat spring having a central axis along the axis, the spring being disposed adjacent to the elastically deformable material and supporting the elastically deformable material in a longitudinal direction. Preferably, the piston further comprises a number of flat support means arranged between the elastically deformable material and the spring, the support means forming an interface between the spring and the elastically deformable material. It is possible to rotate along the Preferably, the support means is configured to rotate from a first position to a second position, in the first position its outer boundary may be contained within the first cross-sectional area and In position 2, its outer boundary may be included within the second cross-sectional area.

According to one embodiment of the present invention, there is provided a combination of a piston and a chamber, the chamber defining an elongated chamber having a longitudinal axis, the chamber having a first cross-sectional area at a first longitudinal position thereof and a second cross-sectional area at a second longitudinal position thereof, the change in the first cross-sectional area being greater than the second cross-sectional area, the change in the cross-sectional area of the chamber being at least substantially continuous between the first and second longitudinal positions, the piston adapted to accommodate the cross-section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber, the piston being rotatably fixed to a common member and supported by a support member and comprising elastically deformable means for sealing against an inner wall of the chamber, the inner wall of the chamber being rotatable between 10° and 40° relative to the longitudinal axis.

According to one embodiment, a combination is provided in which the support member is rotatable at least substantially parallel to the longitudinal axis. Preferably, the common member is attached to the handle for use by an operator, and the support member extends within the chamber in a direction relatively remote from the handle. Preferably, the combination further includes means for biasing the support member against the inner wall of chamber A, the chamber defining an elongate chamber having a longitudinal axis, the chamber A in its first longitudinal position. , the chamber has a first cross-sectional area, and at its second longitudinal position, a second cross-sectional area, the change in cross-sectional area of the chamber is greater than the second cross-sectional area, and the change in cross-sectional area of the chamber is greater than the second cross-sectional area; is at least substantially continuous between a first longitudinal position and a second longitudinal position, the piston being at least substantially continuous between a first longitudinal position and a second longitudinal position, wherein the piston is connected to a first longitudinal position of a chamber containing an elastically deformable container containing a deformable material. adapted to fit the cross-section of the chamber when moving from the directional position to the second longitudinal position.

Preferably, the deformable material is a fluid or mixture of fluids, for example water, steam and/or gas, or a foam. Preferably, in a cross section through the longitudinal direction, the container has a first shape in a first longitudinal direction and a second shape in a second longitudinal direction, the first shape being different from the second shape. Preferably, at least a portion of said deformable material is compressible, said first shape having an area larger than the area of said second shape. Preferably, the deformable material is at least substantially incompressible. Preferably, the piston comprises a chamber in communication with the deformable container, said chamber having a variable volume. Preferably, the volume is
The pressure of the chamber can be varied by an operator. Preferably, the chamber comprises a spring biased piston. Preferably, the combination further comprises means for defining a volume of the chamber such that a pressure of the fluid in the chamber is related to a pressure of the fluid between the piston and the second longitudinal position of the container. Preferably, the defining means is configured to define a pressure in the chamber at least substantially the same as a pressure between the piston and the second longitudinal position of the container. Preferably, the container comprises an elastically deformable material comprising:

Preferably the forcing means comprises fibres. Preferably, the foam or fluid provides a pressure greater than a maximum pressure of the surrounding atmosphere within the container during movement of the piston from the first longitudinal position to the second longitudinal position or vice versa. adapted to do so. Preferably, the chamber defines an elongate chamber having a longitudinal axis, the chamber having a first cross-sectional shape and area at a first longitudinal position thereof and a second cross-sectional shape and area thereof at a second longitudinal position of the chamber. ,No. 2
the first cross-sectional shape is different from the second cross-sectional shape, and the change in the cross-sectional shape of the chamber is between the first longitudinal position and the second longitudinal position. At least substantially continuous, the piston is adapted to conform to the cross-section of the chamber as it moves from the first longitudinal position to the second longitudinal position 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 50%, such as at least 60%, preferably at least 70%, such as at least 80% at least 90% larger than the second cross-sectional area. Preferably, the first cross-sectional shape is at least substantially circular and the second cross-sectional shape is elongated, such as oval, having at least twice the first dimension, the first dimension being at least three, preferably at least four times the dimension at an angle to the first dimension. Preferably, the first cross-sectional shape is at least substantially circular and the second cross-sectional shape comprises at least two or more at least substantially elongated, e.g. lobe-shaped, parts. Preferably, in cross-section at the first longitudinal position, the first circumference of the chamber is 80-120%, such as 85-115%, preferably 90-110, such as 95-105. Preferably, it is 98-102% of the second circumference of the chamber in cross-section in the second longitudinal direction. Preferably, the first and second circumferences are at least substantially identical. Preferably, the piston comprises elastically deformable means rotatably fixed to the common member and supported by the support member for sealing against the inner wall of the chamber. Preferably, the piston comprises an elastically deformable container containing a deformable material.

According to another embodiment of the present invention, there is provided a combination of a piston and a chamber, the chamber defining an elongated chamber having a longitudinal axis, the chamber having a first cross-sectional area at a first longitudinal position thereof and a second cross-sectional area at a second longitudinal position thereof, the change in the first cross-sectional area being greater than the second cross-sectional area, the change in the cross-sectional area of the chamber being at least substantially continuous between the first longitudinal position and the second longitudinal position, the piston comprising an elastically deformable material adapted to conform to the cross-section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber, and a coiled flat spring having a central axis along at least the longitudinal axis, the spring disposed adjacent to the elastically deformable material and supporting the elastically deformable material in the longitudinal direction.

Preferably, the piston further comprises a number of planar support means arranged between the elastically deformable material and the spring, the support means being rotatable along an interface between the spring and the elastically deformable material. Preferably, the support means is configured to rotate from a first position to a second position, in the first position its outer boundary may be contained within said first cross-sectional area and in said second position the outer boundary of said second cross-sectional area may be contained within said second cross-sectional area.

According to one embodiment of the invention, there is provided a combination of a piston and a chamber, the chamber defining an elongated chamber having a longitudinal axis, the piston being movable within the chamber from a first longitudinal position to a second longitudinal position, the chamber having an inner wall that is elastically deformable 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 cross-sectional area at its first longitudinal position when the piston is positioned at its position and a second cross-sectional area at its second longitudinal position when the piston is positioned at its position, the first cross-sectional area being greater than the second cross-sectional area, and the change in cross-sectional area of the chamber is at least substantially continuous between the piston's first longitudinal position and the second longitudinal position.

Preferably, the piston is made of at least substantially incompressible material. Preferably, the piston has a shape tapered in a direction from the second longitudinal position in a cross section along the longitudinal axis. Preferably, the chamber includes 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.

According to one embodiment of the present invention, there is provided a pump for pumping a fluid, said pump comprising a combination as claimed in any one of the claims, means for engaging a piston from a position outside said chamber, a fluid inlet connected to said chamber and including a valve means, and a fluid outlet connected to said chamber.

Preferably, the engagement means have an outer position with the piston in its first longitudinal position and an inner position with the piston in its second longitudinal position. Preferably, the engagement means have an outer position with the piston in its second longitudinal position and an inner position with the piston in its first longitudinal position.

According to an embodiment of the invention, the shock absorber comprises a combination as described above, means for engaging the piston from a position external to the chamber, an external position in which the piston is in a first longitudinal position; is in a second longitudinal position.

Preferably, the shock absorber further includes a fluid inlet connected to the chamber and includes a valve means. Preferably, the shock absorber further includes a fluid outlet connected to the chamber and includes a valve means. Preferably, the chamber and the piston form an at least substantially sealed cavity containing a fluid, the fluid being compressed as the piston moves from the first longitudinal position to the second longitudinal position. Preferably, the shock absorber further includes means for biasing the piston towards the first longitudinal position.

According to one embodiment of the present invention, there is also provided an actuator comprising the above combination, means for engaging the piston from a position outside the chamber, and means for introducing fluid into the chamber to displace the piston between a first longitudinal position and a second longitudinal position.

Preferably, the actuator further comprises a fluid inlet connected to the chamber and including a valve means. Preferably, the actuator further comprises a fluid outlet connected to the chamber and including a valve means. Preferably, the actuator further comprises means for biasing the piston to the first or second longitudinal position. Preferably, the introducing means comprises means for introducing a pressurized fluid into the chamber. Preferably, the introducing means is configured to introduce a combustible fluid, for example petrol or diesel, into the chamber and the actuator further comprises means for combusting the combustible fluid. Preferably, said actuator further comprises a crank configured to convert movement of said piston into rotation of said crank. 207-1 SPECIFICALLY PREFERRED EMBODIMENTS According to one embodiment of the present invention there is provided a piston-chamber combination comprising an elongated chamber (70) bounded by an internal chamber wall (71, 73, 75) and comprising piston means (76, 76', 163) within said chamber, said piston means comprising sealing means sealably movable relative to said chamber at least between first and second longitudinal positions of said chamber, said chamber having cross-sectional areas which differ at least substantially continuously between said first and second longitudinal positions, said chamber having a cross-sectional area which differs at least substantially continuously between said first and second longitudinal positions, said cross-sectional area at said first longitudinal position being greater than said cross-sectional area at said second longitudinal position, said piston means being designed to adapt itself and said sealing means to said different cross-sectional areas of said chamber during relative movement of said pistons.
a means for extending from a first longitudinal position to a second longitudinal position of said chamber, the different cross-sectional areas having different cross-sectional shapes, the change in cross-sectional shape of the chamber (162) being continuous between the first longitudinal position and the second longitudinal position of the chamber (162), the piston means (163) being further designed to accommodate itself and the sealing means to the different cross-sectional shapes, the cylinder (162)
A first circumferential length of the cross-sectional shape at the first longitudinal position is 80-120% of a second circumferential length of the cross-sectional shape of the chamber (162) at a second longitudinal position of the chamber (162).

Preferably, the cross-sectional shape of the chamber (162) at its first longitudinal position is at least substantially circular, and the cross-sectional shape of the chamber (162) at its second longitudinal position is elongated, such as oval, and the first dimension is at least 3.0 mm wide at an angle to the first dimension.
Preferably it is at least 2, such as at least 4 times the dimension. Preferably the cross-sectional shape of the chamber (162) at its first longitudinal position is at least substantially circular and the cross-sectional shape of the chamber (162) at its second longitudinal position comprises at least two or more, e.g. lobe-shaped parts. Preferably it is a. The first circumferential length of the cross-sectional shape of the cylinder (162) at its first longitudinal position is 85-115%, preferably 90-110%, e.g. 95-105, preferably 98-102%, of the second circumferential length of the cross-sectional shape of the chamber (162) at its second longitudinal position. Desirably the first and second circumferential lengths are at least substantially identical.

Preferably, the cross-sectional area of the chamber (162) at the second longitudinal position is less than the cross-sectional area of the chamber (162) at the first longitudinal position.
95% or less of the cross-sectional area of the chamber (162) at the second longitudinal position.
The cross-sectional area of the chamber (162) in the first longitudinal direction is between 95% and 15% of the cross-sectional area of the chamber (162) at its first longitudinal position.

Preferably, the cross-sectional area of the chamber (162) in its second longitudinal position is 95% or less of the cross-sectional area of the chamber (162) in its first longitudinal position. Preferably, the cross-sectional area of the chamber (162) in its second longitudinal position is between 95% and 15% of the cross-sectional area of the chamber (162) in its first longitudinal position. Preferably, the cross-sectional area of the chamber (162) in its second longitudinal position is between 95% and 70% of the cross-sectional area of the chamber (162) in its first longitudinal position. Preferably, the cross-sectional area of the chamber (162) in its second longitudinal position is about 50% of the cross-sectional area of the chamber (162) in its first longitudinal position.

According to an embodiment of the present invention there is also provided a pump for pumping a fluid comprising a combination according to any of the preceding claims, a means for engaging piston means (76, 163) from a position outside the chamber (162), a fluid inlet connected to the chamber and comprising valve means, and a fluid outlet connected to the chamber (162).

Preferably, the engagement means has an outer position in which the piston means (76, 163) is located at a first longitudinal position of the chamber, and an inner position in which the piston means (76, 163) is located at a second longitudinal position of the chamber (162).

Preferably the engagement means has an outer position in which the piston means (76, 163) is located at the second longitudinal position of the chamber and an inner position in which the piston means (76, 163) is located at the first longitudinal position of the chamber (162).

According to one embodiment of the invention, a shock absorber is also provided. The shock absorber comprises a combination according to any one of claims 1 to 9 and means for engaging the piston means (76, 163) from a position outside the chamber, the engaging means comprising: The piston means is the first
an outer position in which the piston means is in a second longitudinal position; and an inner position in which the piston means is in a second longitudinal position.

Preferably, the shock absorber comprises a fluid inlet connected to the chamber (162) and provided with a valve means.
Preferably, the shock absorber further comprises a fluid outlet connected to the chamber (162) and comprising a valve means. Preferably, the chamber (162) and the piston means (76, 163) define an at least substantially enclosed cavity containing a fluid, and the fluid is compressed as the piston means moves from the first longitudinal position of the chamber (162) to the second longitudinal position. Preferably, the shock absorber further comprises means for biasing the piston means towards the first longitudinal position of the chamber.

According to one embodiment of the invention, an actuator is also provided. The actuator comprises a combination according to any of claims 1 to 9, means (162) for engaging the piston means from a position external to the chamber, and between a first and second longitudinal position of the chamber. Means are provided for introducing fluid into the chamber (162) in order to displace the piston means (76, 163).

Preferably, the actuator further comprises a fluid inlet connected to the chamber (162) and comprising a valve means. Preferably, the actuator further comprises a fluid outlet connected to the chamber and comprising a 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 actuator wherein the introducing means comprises means for introducing pressurized fluid into the chamber (162). Preferably, the introducing means is adapted to introduce a combustible fluid, such as petrol or diesel, into the chamber (162), the actuator further comprising means for combusting the combustible fluid. Preferably, the actuator further comprises a crank adapted to convert translation of the piston means into rotation of the crank.
653 SUMMARY OF THE DISCLOSURE In a first aspect, the present invention relates to a piston and chamber combination, comprising:
The container is elastically expandable such that it has a perimeter in a stress-free, undeformed manufactured size state that is approximately the perimeter of an inner chamber wall of the container in the second vertical position.

In this context, the cross section is preferably taken perpendicular to the longitudinal axis (=transverse direction).
Preferably, the second cross-sectional area is 98-5%, such as 95-70%, of the first cross-sectional area. In certain situations, the second cross-sectional area is about 50% of the first cross-sectional area.

Many different techniques can be used to achieve this combination, which are further described in relation to subsequent aspects of the invention.
One such technique is where the piston comprises a container containing a deformable material. In such a situation, the deformable material may be a fluid or a mixture of fluids such as water, steam, and/or gas, or a foam. This material, or a portion thereof, may be compressible, such as a gas or a mixture of water and gas, or may be at least substantially incompressible.

The deformable material may also be a spring force actuated device, such as a spring. Thus, the container may be adjustable to provide seals to chamber walls having different cross-sectional areas and different circumferential sizes. This is done by selecting a production size of the piston (unstressed, undeformed) approximately equal to the circumferential length of the smallest cross-sectional area of the chamber, and placing it in a longitudinal position with a larger circumferential length. This can be accomplished by expanding the piston as it moves and contracting it as it moves in the opposite direction.

This can also be achieved by providing a means to maintain a certain sealing force from the piston on the walls of the chamber, maintaining the internal pressure of the piston at a predefined level that can be kept constant during the stroke. The pressure level of a certain magnitude depends on the difference in the circumferential length of the cross section and the possibility of obtaining a suitable seal at the cross section with the smallest circumferential length. If the difference is large and the appropriate pressure level is too high to obtain a suitable sealing force at the smallest circumferential length, a change in pressure can be arranged during the stroke. This requires pressure management of the piston. Since commercially used materials are usually not solid, there must be a possibility to maintain this pressure, for example by using a valve for expansion purposes, especially when very high pressures are used. If a spring force actuator is used to obtain the pressure, a valve may not be necessary.

When the cross-sectional area of the chamber changes, the volume of the container can change. Thus, in the longitudinal cross-section of the chamber, the container can have a first shape in a first longitudinal direction and a second shape in a second longitudinal direction, the first shape being different from the second shape. In one situation, at least in part, the deformable material is compressible, the first shape having an area larger than the area of the second shape. In such a situation, the overall volume of the container changes, and the fluid must be compressible. Alternatively, or optionally, the piston can include an enclosed space in communication with the deformable container, the enclosed space having a variable volume. In this way, the enclosed space can take in fluid or expel fluid as the deformable container changes volume. The change in the volume of the container is automatically adjustable. The pressure in the container can be constant during the stroke.

The enclosed space may also include a spring-loaded piston. This spring may define the pressure within the piston. The volume of the enclosed space can be varied. In this way, the overall pressure or the maximum/minimum pressure of the container can be changed.

When the closed space is divided upwardly into a first closed space and a second closed space, said space is such that the pressure of the fluid in said first closed space is equal to or lower than said second closed space. The method further includes means for defining a volume of the first enclosed space so as to be related to the pressure within the enclosed space. Said space is expandable, for example, by means of a valve, preferably an expansion valve, such as a Schrader valve. A possible pressure drop within the container, for example due to leakage through the walls of the container, may be balanced by expansion of the second enclosed space through the defining means. The defining means may be a pair of pistons, the pair of pistons being in each enclosed space.

The defining means may be configured to define the first enclosed space and the pressure within the container to be at least substantially constant during the stroke. However, any kind of pressure level within the container can be defined by means of definition, for example when the wall of the container expands when the piston moves to a large cross-sectional area in the first longitudinal position. A pressure increase may be required, in which case the contact area and/or contact pressure at the current pressure value may be too small to maintain a proper seal, and the defining means is It may be a pair of pistons, one inside each. The second enclosed space can be expanded to a certain pressure level so that despite the volume, a pressure increase can be transmitted to the first enclosed space and the container.

The vessel, and therefore the second closed space, can also be larger. This can be achieved, for example, by a combination of a piston and a chamber (second closed space) with different cross-sectional areas in the piston rod. The pressure drop can also be engineered.

Pressure management of the piston may also be achieved by relating the pressure of the fluid within the enclosed space to the pressure of the fluid within the chamber. By providing a means for defining the volume of an enclosed space communicating with the chamber. In this way, the pressure in the deformable container can be varied to obtain a proper seal. For example, a simple method is to provide the defining means to increase the pressure in the enclosed space when the container is moving from the second longitudinal position to the first longitudinal position. In this situation, a simple piston can be provided between the two pressures (as it does not loosen any of the fluid in the deformable container).

In fact, the use of this piston can define any relationship between pressures, in that the chamber in which the piston translates can be tapered in the same way as the main chamber of the combination.

A device that can be moved directly from the piston rod into the container can also change the volume and/or pressure in the container. It is also possible that the piston does not have a valve for expansion or does not communicate with it (closed system). If the piston does not have an expansion valve, the fluid may be impermeable to the material of the container wall. A step in the installation process may be a step of permanently closing the container volume after the fluid has been placed in the volume of the piston and after positioning in the second longitudinal position of the chamber. The speed of the piston can be obtained depending on the possibility of a large fluid flow with not too much friction between it and the first closed chamber. If the piston has an expansion valve, the container wall may be permeable to the fluid.

The container can be expanded by a pressure source contained in the piston. or an external pressure source where the outside of the combination and/or the chamber itself is an external pressure source. All solutions require a valve in communication with the piston. This valve may preferably be an expansion valve, a Schrader valve, or a valve that generally has a spring force operated valve core. A Schrader valve has a spring-loaded valve core pin that closes regardless of pressure within the piston, allowing all types of fluids to flow through it. However, other types of valves may also be used, for example check valves.

The container can be inflated through an enclosed space in which a spring-loaded synchronized piston acts as a check valve. The fluid may flow from a pressure source, eg an external pressure source, or eg an internal pressure vessel, through a longitudinal duct in the bearing of the piston rod of the spring-loaded piston.

If the enclosed space is divided into a first and a second enclosed space, the expansion may be performed using the chamber as a pressure source, since the second enclosed space may prohibit expansion into the first enclosed space through it. It can be carried out. The chamber may have an inlet valve in the foot of the chamber. To inflate the container, an expansion valve, for example a valve having a spring force actuated valve core, such as a Schrader valve, can be used in conjunction with an actuator. This may be an actuating pin according to WO 96/10903 or WO 97/43570, or a valve according to WO 99/26002 or US Pat. No. 5,094,263. It may also be an actuator. The core pin of the valve is moving towards the chamber as it closes. The actuation pin from the above-mentioned WO document has the advantage that the opening force of the spring-actuated valve core is very low and it can be easily inflated by a manually actuated pump. The actuators cited in the US patents may require the power of a conventional compressor.

If the working pressure in the chamber is higher than the pressure in the piston, the piston can be expanded automatically. If the working pressure in the chamber is lower than the pressure in the piston, a higher pressure must be obtained, for example by temporarily closing an outlet valve in the foot of the chamber. If the valve is, for example, a Schrader valve that can be opened by a valve actuator according to WO 99/26002, this can be achieved by creating a bypass in the form of a chamber, by connecting the chamber and the space between the valve actuator and the core pin of the valve. This bypass can be opened (the Schrader valve can remain closed) and closed (the Schrader valve can open) and can be achieved, for example, by a movable piston. The movement of this piston can be arranged manually, for example, by a pedal, which is moved by the operator from an inactive position to an active position and vice versa. It can also be achieved by other means, such as an actuator initiated by the result of a pressure measurement in the chamber and/or in the container.

Obtaining the predetermined pressure in the vessel can be achieved manually, for example by a pressure gauge, such as a manometer, measuring the pressure in the vessel, informing the operator. It can also be achieved automatically, for example by a release valve in the vessel, which releases the fluid when the pressure of the fluid exceeds a maximum pressure setting. It can also be achieved by a spring-force actuated cap, which closes the channel from the pressure source above the valve actuator when the pressure exceeds a predetermined pressure value. Another solution requires a pressure measurement in the corresponding solution-vessel of a closable bypass of the outlet valve of the chamber, which can be operated at a predetermined pressure value by an actuator that opens or closes the bypass of the valve actuator according to WO 99/26002, for example, of the Schrader valve of the vessel.

The above solution is also applicable to any piston containing a container. What is shown in WO 00/65235 pamphlet and WO 00/70227 pamphlet. One such technique is for the piston to include a container that includes an elastically deformable container wall.

Expansion or contraction of the container wall initiated by a change in the size of the circumferential length of the cross section can be enabled by selecting reinforcements that expand or contract the container wall in three dimensions. Therefore, no excess material remains between the walls of the container and the walls of the chamber. Resisting the influence of pressure in the chamber on the piston (longitudinal extension) in order to limit the contact length can also be done by selecting suitable reinforcements. Container wall reinforcement may and/or may not be located within the container wall.

The reinforcement of the container wall can be made of a woven material. This can be one layer, but preferably at least two layers crossing each other, so that the reinforcement can be easier to install. These layers can be, for example, woven or knitted. If the woven threads are arranged in different layers close to each other, the threads can be made of an elastic material. These layers can be, for example, vulcanized in two layers of an elastic material, such as rubber. When the container is at production size, the elastic material of the wall as well as the reinforcing bars are stress-free and do not deform. The expansion of the container's reinforced wall means that as the threads expand, the distance between the intersections (= seam size) increases, and as they contract, the seam size decreases.

Sealing of the contracting vessel walls to the chamber walls can be established by pressurizing the vessel to a certain pressure, where the threads are slightly expanded so that the seam size increases slightly. The contact of the vessel walls prohibits the internal pressure from expanding the vessel in such a way that the contact length becomes too large, thus avoiding its obstruction.

The stockinette rebar may be made of elastic threads and/or elastically bendable threads, for example. Inflation of the walls of the container can be carried out by stretching the knitted bent loops. When the container wall contracts, the stretched loops may return to their undeformed state.

Woven fabric reinforcement may be manufactured on a production line where the woven or knitted fabric reinforcement is placed as a cylinder inside two layers of elastic material. Inside the smallest cylinder is placed a bar on which the caps are held in sequence top-down top-down, and these can move on the bar. At the end of the line is held a vulcanization oven. The inside of the oven can have the size and shape of the container in a stress-free, unformed state. The part of the cylinder that is in the oven is cut lengthwise and two caps are placed in the cylinder at both ends and held there. The oven is closed and steam above 100°C and high pressure is introduced. After about 1-2 minutes the oven may be opened and the two caps vulcanized to the walls of the container. There may be multiple ovens, for example rotating or translating, and all ending at the end of the production line, to use the lead time of the vulcanization. It is also possible to have multiple ovens on the production line itself, using the transportation lead time as the vulcanization time.

The same applies to the manufacture of fiber-reinforced walls of containers. Reinforced fibers can be produced, for example, by injection molding. By cutting the assembled socket, or string, the assembled socket is then placed at both ends. Both options can easily be serialized. For the rest, the manufacturing process is similar to that described above for textile reinforcement.

The piston with the elastically deformable container may also comprise a reinforcing means not located in the wall, for example a number of resilient arms connected to the wall of the container and which may or may not be expandable. If expandable, the reinforcing means also serve to limit the deformation of the wall of the container due to the pressure in the chamber.

Another option is external reinforcement of the walls of the container.
Another aspect of the invention relates to a piston and chamber combination, the chamber defining an elongated chamber having a longitudinal axis, the piston extending from the chamber from at least a second longitudinal position to a first longitudinal position. movable within the first longitudinal position and the second
an elastically deformable inner wall along at least a portion of the inner chamber wall between the longitudinal positions; area, and a second cross-sectional area at a second longitudinal position when the piston is positioned at that position, the first cross-sectional area being greater than the second cross-sectional area, a change in cross-section of the chamber; is at least substantially continuous between the first longitudinal position and the second longitudinal position when the piston is moved between the first longitudinal position and the second longitudinal position. ing.

Therefore, alternatively to a combination in which the piston adapts to changes in the cross section of the chamber, this aspect relates to a chamber with adaptability. Naturally, the piston can be made of an at least substantially incompressible material or a combination of an adaptable chamber and an adaptable piston, such as the piston according to the above aspect.

Preferably, the piston has a shape, in cross section along the longitudinal axis, that tapers towards the second longitudinal position.
A preferred method of providing a compliant chamber is to construct the chamber to include an outer support structure surrounding an inner wall, and a fluid that is retained by the space defined by the outer support structure and the inner wall. In that way, the choice of fluid or combination of fluids helps define the characteristics of the chamber, such as the seal between the wall and the piston, and the force required.

In yet another aspect, the invention relates to a piston and chamber combination. the chamber defines an elongated chamber having a longitudinal axis and has a first cross-sectional shape and area at the first longitudinal position and a second cross-sectional shape and area at the second longitudinal position; The first cross-sectional shape is different from the second cross-sectional shape, and the change in the cross-sectional shape of the chamber is different from the second cross-sectional shape.
at least substantially continuous between the longitudinal position of the piston and the second longitudinal position of the piston;
It is adapted to accommodate the cross section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber.

This very interesting aspect is based on the fact that different shapes of geometric figures, for example, have various relationships between the circumference and its area. Also, the transition between two shapes is
This may be done sequentially so that the chamber can have one cross-sectional shape at one longitudinal location thereof and another cross-sectional shape at another longitudinal location thereof while maintaining a desired smooth transition of the surface within the chamber.

In this context, the shape of a cross section is the overall shape, regardless of its size. Two circles have the same shape even though one has a different diameter from the other.
Preferably, the first cross-sectional area is at least 2%, such as 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%, such as at least 90%, preferably at least 95%.

In a preferred embodiment, the first cross-sectional shape is at least substantially circular and the second cross-sectional shape is elongated, such as oval, and has at least two first dimensions, the first dimension being at an angle to the first dimension and at least three, preferably at least four times the dimension.

In another preferred embodiment, the first cross-sectional shape is at least substantially circular and the second cross-sectional shape comprises at least two or more at least substantially elongated, eg lobe-shaped sections.

Some advantages are seen if the first circumference of the chamber in cross section at the first longitudinal position is 80-120%, for example 85-115%, preferably 90-110, for example 95-105, preferably 98-102%, of the second circumference of the chamber in cross section at the second longitudinal position. Problems may arise when trying to seal against walls with different dimensions due to the fact that the sealing material provides a sufficient seal and should its dimensions be changed. If the circumference only changes slightly, as is the situation in the preferred embodiment, the seal can be more easily controlled. Preferably, the first and second circumferences are at least substantially identical, so that the sealing material is only bent and not stretched to a significant extent.

Alternatively, when bending or deforming the sealing material, it may be desirable for the circumference to change slightly, for example in that when bent, one side of it is compressed and the other side is stretched. Overall, it is desirable that at least the seal material automatically "selects" to provide a desired shape close to the circumference.

One type of piston that may be used in this type of combination is one that includes a deformable container. The container may be elastically or inelastically deformable. In the last method, the walls of the container may bend during movement within the chamber. An elastically deformable container with a manufacturing size approximately the size of the circumference of the first longitudinal position of the chamber, with a reinforcement type that allows contraction with high frictional forces, is also used in this type of combination. It can be used especially at high piston speeds.

An elastically deformable container having a manufacturing size approximately the size of the perimeter of the second longitudinal position of the chamber may also be used, with a type of skin reinforcement allowing for portions of the container wall to have different distances from the central axis of the chamber in the longitudinal cross section of the chamber.

It is clear that depending on where the combination is found, one of the piston and the chamber may be stationary, the other moving, or both moving. This does not affect the function of the combination.

The piston may also slide over an inner wall and an outer wall, the inner wall may have a tapered shape and the outer wall may be cylindrical.
Naturally, the combination of the present invention can be used for many purposes, mainly focusing on the novel method of providing an additional way of adjusting the translation of the piston to the force required/to be taken. In fact, the cross-sectional area/shape can be varied along the length of the chamber to adapt the combination for a specific purpose and/or force. One purpose is to provide a pump for use by women and teenagers, which should still be able to exert a constant pressure. In such a situation, an ergonomically improved pump is required by determining the force a person can exert at any position of the piston, thereby providing the chamber with the appropriate cross-sectional area/shape.
Give shape.

Another use of this combination is for shock absorbers which would determine the range/shape that would be required for a particular shock (force) travel.Also, an actuator may be provided where the amount of fluid introduced into the chamber provides different travel of the piston depending on the actual position of the piston prior to the introduction of the fluid.

In fact, the nature of the piston, the relative position of the first and second longitudinal positions, and the arrangement of any valves connected to the chamber can result in pumps, motors, actuators, shock absorbers with different pressure characteristics and different force characteristics. etc. can be provided.

A preferred embodiment of the chamber and piston combination is described as an example for use in a piston pump. However, this is primarily the valve arrangement of the chamber and also what article or medium starts moving, which is crucial for the type of application such as a pump, actuator, shock absorber or motor. Therefore, the scope of application of the present invention should not be limited to the above uses. A piston pump allows medium to be drawn into the chamber.

It can then be closed by a valve arrangement. The medium may be compressed by the movement of the chamber and/or the piston, and then the valve may release this compressed medium from the chamber. In an actuator, the valve arrangement may press the medium into the chamber, moving the piston and/or the chamber to initiate the movement of the attached device. In a shock absorber, the chamber may be completely closed and the compressible medium may be compressed by the movement of the chamber and/or the piston. In this case, a non-compressible medium may be placed in the chamber, for example the piston may be provided with several small channels that can create dynamic friction to slow down the movement.

Furthermore, the present invention can use a medium to move the piston and/or chamber, which can also be used in propulsion applications, for example, to turn a shaft like a motor. Any type of principle according to the present invention can be applied to all of the above applications.

The principles of the present invention may be used in pneumatic and/or hydraulic applications other than the piston pumps described above.
The present invention therefore also relates to a pump for pumping a fluid, the pump being configured to include a combination according to any of the above aspects, a means for engaging the piston from a position outside the chamber, a fluid inlet connected to the chamber and provided with a valve means, and a fluid outlet connected to the chamber.

In one situation, the engagement means can have an outer position where the piston is in its first longitudinal position and an inner position where the piston is in its second longitudinal position. This type of pump is preferred where pressurized fluid is desired.

In other situations, the engagement means may have an outer position where the piston is in its second longitudinal position and an inner position where the piston is in its first longitudinal position. This type of pump is preferred where substantial pressure is not desired but simply to transport fluid.

In a situation where the pump is configured to stand on the floor and the piston/engagement means is configured to forcefully compress a fluid such as air downwards, the maximum force may be ergonomically provided at the lowest position of the piston/engagement means/handle. Thus, in the first situation, this means that the highest pressure is provided there. In the second situation, this simply means that the largest area, and therefore the largest volume, is found at the lowest position. However, due to the fact that a pressure that exceeds the tire pressure is required to open the tire valve, for example, it is desirable to provide the smallest cross-sectional area just before the lowest position of the engagement means, so that more fluid is forced into the tire by opening the valve and providing a larger cross-sectional area.

The pump according to the invention can use substantially less working force than a comparable pump based on a conventional piston-cylinder combination, so that for example a water pump can extra suck water from a greater depth. This feature is very important, for example in least developed countries. Also, when pumping liquids when the pressure difference is almost zero, the chamber according to the invention may have another function. It can be adapted to the physical needs of the user (ergonomics) by a suitable design of the chamber, for example according to Fig. 17B and Fig. 17A, respectively, as if a pressure difference was present. This can also be achieved by the use of valves.

The invention also relates to a piston that seals in a cylinder, and at the same time to a tapered cylinder. The piston may or may not comprise an elastically deformable container. The resulting chambers may be of the type with different circumferential sizes of cross-sectional areas, or they may be identical. The piston may comprise one of a number of piston rods. The outer cylinder may also be cylindrical or tapered.

The invention also relates to a shock absorber. The shock absorber comprises a combination according to any of the aspects of the combination, means for engaging the piston from a position outside the chamber, said engaging means having an outer position where the piston is in its first longitudinal position and an inner position where the piston is in its second longitudinal position. The absorber further comprises a fluid inlet connected to the chamber and may comprise a valve means. The absorber may also comprise a fluid outlet connected to the chamber and may comprise a valve means. The chamber and the piston preferably form an at least substantially sealed cavity containing a fluid, the fluid being compressed when the piston moves from the first longitudinal position to the second longitudinal position. Typically the absorber comprises means for biasing the piston towards the first longitudinal position.

The invention also relates to an actuator. The actuator comprises a combination according to any of the aspects of the combination, means for engaging the piston from a position outside the chamber, and means for introducing a fluid into the chamber to displace the piston between a first longitudinal position and a second longitudinal position. The actuator may comprise a fluid inlet connected to the chamber and comprising a valve means. There may also be a fluid outlet connected to the chamber and including a valve means. Additionally, the actuator may comprise means for biasing the piston to the first or second longitudinal position.

The present invention also relates to a motor including a combination according to any of the above combination aspects.
Finally, the invention also relates to a power supply unit, which may be mobile, for example by a M(mobile) P(wower) U(nit), preferably by parachute. Such a unit may comprise any kind of power supply, preferably at least one set of solar vend power supply, and a power device, such as a motor according to the invention. There may also be at least one service device, such as a pump according to the invention, and/or any other device that utilizes excess energy obtained from the low working force of the device comprising the piston and chamber combination according to the invention. Due to the very low working force, the configuration of the device according to the invention may be constructed with a lighter weight than those based on conventional piston-cylinder combinations, so that it may be possible to transport the MPU by parachute.

The various embodiments described above are provided by way of example only and should not be construed as limiting the present invention. Those skilled in the art will readily recognize various modifications, variations and combinations of elements that may be made to the present invention without strictly adhering to the exemplary embodiments and applications shown and described herein without departing from the true spirit and scope of the present invention.

All types of pistons, and in particular containers with elastically deformable walls, may be sealingly connected to the chamber walls during movement between longitudinal positions, engagingly connected to the chamber walls, or not connected; or may engage and sealingly connect to the chamber walls. Furthermore, it is possible that there is no engagement between any of said walls, and that the walls come into contact with each other. This occurs, for example, when the container is moving from a first longitudinal position to a second longitudinal position within the chamber.

The type of connection between the walls (sealing and/or engaging and/or contacting and/or no connection) can be achieved by using the correct internal pressure within the vessel walls, i.e. high pressure for a sealable connection, low pressure for engaging, and atmospheric pressure for no connection (production size vessels), therefore vessels with a sealed space are preferred as the sealed space allows the pressure within the vessel to be controlled from the outside position of the piston.

Another option for the mating connection is a thin wall of the container, which has reinforcements protruding from the surface of said wall so that leakage can occur between the container wall and the chamber wall. It can have material.
653 Particularly Preferred Embodiments According to one embodiment of the invention, the invention comprises an elongated chamber bounded by an internal chamber wall, a piston within the chamber, and a first longitudinal position of the chamber and a second longitudinal position of the chamber. the chamber is sealably movable with respect to at least the chamber wall between positions, the chamber at an intermediate longitudinal position between the first longitudinal position and the second longitudinal position; having a cross-sectional area of a different cross-sectional area and a different circumferential length, at least substantially continuously different cross-sectional areas and circumferential lengths, the cross-sectional area and the circumferential direction at the second longitudinal position; the length is less than the cross-sectional area and circumferential length at the first longitudinal position, and the piston is elastically deformable to thereby accommodate different cross-sectional areas and circumferential lengths of the piston. A piston-chamber combination with a container provided is provided. equal to said different cross-sectional area and different circumferential length of the chamber during relative movement of the piston between a first longitudinal position and a second longitudinal position through said intermediate longitudinal position; adapting something
The piston has a circumferential length that is approximately equal to a circumferential length of the chamber (162, 186, 231) in the second longitudinal direction, and the piston has a circumferential length that is substantially equal to the circumferential length of the chamber (162, 186, 231) in the second longitudinal direction. expandable from a manufacturing size, whereby said second portion of said piston
the chamber is manufactured to have a manufacturing size of the chamber that allows expansion of the piston from the manufacturing size of the piston during relative movement from the longitudinal direction of the piston to the first longitudinal direction; chamber.

Preferably, the container is expandable, said container being elastically deformable and expandable to provide different cross-sectional areas and circumferential lengths of the piston. Preferably, the cross-sectional area of the chamber at its second longitudinal position is between 98% and 5% of the cross-sectional area of the chamber at its first longitudinal position. Preferably, 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. Preferably, the cross-sectional area of the chamber at the second longitudinal position is about 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 of fluids, such as water, steam and/or gas, or a foam. Preferably, it is a deformable material that includes a spring force actuation device, such as a spring. Preferably, the container, when placed in the first longitudinal position of the chamber, has, in a cross-section through the longitudinal direction, the second shape of the container when placed in the second longitudinal position of said chamber. have different first shapes. Preferably, at least a portion of the deformable material is compressible and the first shape has a larger area than the area of the second shape. Preferably the deformable material is at least substantially incompressible. Preferably, the container is inflatable to a predetermined pressure value. Preferably the pressure remains constant during the stroke. Preferably, the piston comprises an enclosed space communicating with the deformable container, the enclosed space having a variable volume. Preferably, the volume of the closed space is adjustable. Preferably a first enclosed space comprising a spring-loaded pressure-tuned piston.

Preferably, the device further comprises means for defining the volume of said first enclosed space such that the pressure of the fluid in said first enclosed space is related to the pressure in said second enclosed space. Preferably, the defining means is configured to define the pressure in the first enclosed space during a stroke. Preferably, the defining means is adapted to define the pressure in the first enclosed space at least substantially constant during a stroke. Preferably, the spring biased pressure tuned piston is a check valve through which fluid of an external pressure source can flow into the first enclosed space. Preferably, fluid from an external pressure source can enter the second enclosed space via an expansion valve, preferably a valve having a spring biased core pin such as a Schrader valve from an external pressure source. Preferably, the piston is in communication with at least one valve. Preferably,
The piston comprises a pressure source. Preferably, the valve is an expansion valve, preferably a valve having a spring biased core pin such as a Schrader valve. Preferably, the valve is a check valve. Preferably, the foot of the chamber is connected to at least one valve.

Preferably the outlet valve is an expansion valve, preferably a valve having a spring biased core pin such as a Schrader valve, said core pin moving towards the chamber when closing the valve. Preferably, it is a core pin of a valve connected to an actuator that opens and closes the valve.

Preferably, the actuator comprises a housing connected to a source of pressure medium, said housing having a coupling for receiving a valve to be actuated, a cylinder surrounded by a cylinder wall of a predetermined cylinder wall diameter and having a second cylinder end remote from said first cylinder wall end, a piston movably disposed within said cylinder and fixedly connected to an actuation pin for engaging said spring actuated valve core pin of the valve received in said coupling, and when said piston is moved to a first piston position which is a first predetermined distance from said first cylinder end:
1. A valve actuator for actuating a valve having a spring-actuated valve core pin, wherein when the first piston is moved to the first piston position, the transmission of the pressure medium between the piston and the coupling is inhibited when the second piston is moved to the second piston position, the valve actuator comprising: a first cylinder end, a second cylinder end spaced apart by a second distance greater than the first distance;
The conductive channel is disposed in the cylinder wall and opens into the cylinder at a cylinder wall portion having the predetermined cylinder wall diameter, and the piston has a first cylinder end including a piston ring having a sealing edge that sealably mates with the cylinder wall portion, thereby preventing conduction of pressure medium into the channel in the second position of the piston and opening the channel in the first position of the piston.

Preferably, the actuator is a valve actuator for actuating a valve having a spring actuated valve core pin having a housing connected to a pressure medium source, a coupling for receiving a valve to be actuated, a second cylinder end circumferentially surrounded by a cylinder wall of a predetermined cylinder wall diameter and connected to the housing for receiving pressure medium from the pressure source at a distance from said first cylinder end, a piston movably disposed within said cylinder and fixedly coupled to an actuation pin for engaging a spring actuated valve core pin of a valve received at said coupling, and a conductive channel between said second cylinder end and said coupling for conducting pressure medium from said second cylinder end to said coupling when said piston is moved to a first piston position which is a predetermined distance from said first cylinder. Conduction of the pressure medium between the second cylinder end When the piston is moved to a second piston position at a second predetermined distance from the first piston end that is greater than the first piston distance, the conduction channel is disposed in the cylinder wall, the cylinder wall having a groove portion opening into the cylinder at the cylinder wall portion having the predetermined cylinder wall diameter, the piston is provided with a piston ring having a sealing edge that sealably fits with the cylinder wall portion, the sealing edge of the piston ring being located between the groove portion and the second cylinder end at the second piston position, thereby preventing the conduction of the pressure medium from the second cylinder end to the first cylinder end and the first cylinder end at the second piston position, thereby preventing a coupling opening the groove to the second cylinder end at the first piston position.

Preferably, an actuator valve for a container piston pressure management system selectively supplies pressurized air to an interior of a container piston, the valve being configured to selectively supply pressurized air to an interior of a container piston. a valve body having a cylindrical central passageway opening into both sides, and a spring-loaded check valve securely within said central passageway that blocks said central passageway when closed and allows fluid flow when opened. and a receiving valve body.

a spring-loaded piston slidably received within the passageway above the check valve, the spring-loaded piston sliding toward the check valve from an off position when the pressurized fluid is applied; sliding toward the on position again when pressurized fluid is removed, and the piston is provided with a surface of the central passageway sufficient to prevent leakage of pressurized fluid between the piston and the central passageway surface. a piston and a stem carried by the piston and engageable with the check valve, the piston having a clearance, but sufficient clearance to permit unrestricted sliding; , when the piston moves to the on position, a fixed plug disposed in the central passageway between the check valve and the interior of the canned piston, the stem being spaced generally axially from the piston. a stationary plug extending beyond the piston and abutting the piston when the piston is in the on position, the plug having a ventilation passageway in the space between the plug and the piston at the vent from the atmosphere; Plug A point radially near the stem that prevents pressurized fluid passing through the piston from being compressed between the piston and the piston. a circular compression seal surrounding the vent point that is compressed between the piston and the plug when the check valve is open; This prevents it from being discharged inside.

Preferably, an actuator valve of a container piston pressure management system for selectively supplying pressurized fluid to an interior of a container piston, the valve being configured to selectively supply pressurized fluid to an interior of a container piston. a valve body having a cylindrical central passage opening that selectively supplies pressurized fluid to both the valve body and the valve body that blocks said central passage when closed and allows fluid flow when opened; a spring-loaded check valve securely received within the central passageway; and a spring-loaded check valve slidably received within the passageway above the check valve from an off position when the pressurized fluid is supplied; The piston slides back to the on position when pressurized fluid is applied, and the piston has sufficient clearance between the piston and the central passageway surface to prevent leakage of pressurized fluid. said actuator valve having said actuator valve engaged with a surface of said central passage having a clearance sufficient to prevent leakage of pressurized fluid between said piston, said piston being carried by said piston; actuator valve with a stem that engaging the check valve to open the check valve and permit passage of pressurized fluid into the check valve and the vessel-shaped piston; the piston moves to the on position and engages the outer annular disc; , an inner annular disk abutting the central passage, the piston forming a plug between the check valve and a piston from which the stem extends, the piston being generally axially spaced from the outer disk. but in contact with the piston in the on position, the outer disc having a series of holes in a series of notches in the inner disc radially proximal to the stem opening, and the outer disc has a series of holes radially proximate to the stem opening, and the outer disc has a series of holes in a series of notches in the inner disc and is in contact with the piston. a vent passageway extending from the atmosphere in the space between, so that as the piston moves, pressurized fluid escaping past the piston is compressed between the plug and the piston to resume its movement. Make sure not to. and surrounding the hole when the piston abuts between the piston and the plug so that pressurized fluid leaking past the piston cannot be released to the atmosphere when the check valve is open. Has a circular compression seal.

Preferably, it comprises a housing connected to a pressure source, in the housing a connection hole having a central axis and an inner diameter approximately corresponding to the outer diameter of the expansion valve to which the actuation pin is connected; a cylinder and means for directing a liquid medium to and from a source, the actuating pin being arranged to engage a central spring force actuating core pin of the expansion valve, and the coupling hole being coaxial with the central axis. a piston portion disposed in succession within the housing and having a piston, the piston portion being disposed within a cylinder movable between a first piston position and a second piston position; , a channel, and the piston portion is an actuation pin connected to an expansion valve, the piston portion having a first end and a second end. located at the first end and having an opening at the first end, the valve portion can be guided by a difference in forces acting on the surface of the valve portion and the first valve position. No. 2
valve position, said first valve position leaves said opening open, said second valve position closes said opening, and the upper part of the piston portion closes the valve of the sealing surface of said valve means. form a locus.

Preferably, the valve actuator is a cylinder having a connecting hole for connecting with an expansion valve, the connecting hole having a central axis and an outer opening, positioning means for positioning the expansion valve when connected to the connecting hole, an actuating pin arranged coaxially with the connecting hole for pressing a central spring-force actuated core pin of the expansion valve, and a cylinder wall with a pressure port connected to a pressure source, wherein the actuating pin is shiftable between the proximal pin position and the distal pin position relative to the positioning means so as to press the core pin of the expansion valve to its distal pin position and release the core pin of the expansion valve at its proximal pin position when the expansion valve is positioned by the positioning means, and the actuating pin is connected to a piston, the piston being slidably arranged within the cylinder. A distal piston position corresponding to a proximal pin position is movable between a proximal piston position corresponding to a distal pin position, the piston being disposed in a cylinder between the pressure port and the connecting bore, and being drivable from the proximal piston position to the distal piston position by pressure supplied from a pressure source into the cylinder, and a flow regulating means is provided for selectively interrupting or releasing a flow path between the pressure source and the connecting bore depending on the piston position, adapted so that at least when the expansion valve is positioned by the positioning means, the flow path is interrupted at the proximal piston position and the flow path is released at the distal piston position.

Preferably, the piston is provided with means for obtaining a predetermined pressure level. Preferably the valve is a release valve. Preferably it is a spring force actuated cap which closes the channel above the valve actuator when the pressure exceeds a predetermined pressure value. Preferably, the chambers are opened and closed, the chambers are connected, the space between the valve actuator and the core pin is connected, the piston is movable between an open position and a closed position of said channel, and the movement of the piston is controlled by the piston. controlled by an actuator that is steered as a result of measuring the pressure within. Preferably, a channel connecting the chamber and the space between the valve actuator and the core pin is opened and closed. Preferably, the piston is movable between an open position and a closed position of the channel. Preferably, the piston is operated by an operator control pedal that rotates the shaft from an inactive position to an active position and vice versa. Preferably, the piston is controlled by an actuator that is steered as a result of measuring the pressure within the piston. Preferably, the combination further includes means for defining the volume of the enclosed space such that the pressure of the fluid within the enclosed space is related to the pressure acting on the piston during the stroke. Preferably so as to provide a pressure higher than a maximum pressure of the surrounding atmosphere during movement of the piston from the second longitudinal position of the chamber to the first longitudinal position of the chamber or vice versa within the container. Adapted foam or fluid.

Preferably, the combination includes 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 through an outlet valve and an inlet valve. Preferably, the outlet valve is an expansion valve, preferably a valve having a spring-loaded core pin, such as a Schrader valve, said core pin moving towards a source of pressure when closing the valve. . Preferably, the inlet valve is an expansion valve, preferably a valve having a spring-loaded core pin, such as a Schrader valve, said core pin moving towards the container when closing the valve. Preferably, a channel connecting the chamber and the space between the valve actuator and the core pin is opened and closed.

Preferably, a channel connecting the chamber and the space between the valve actuator and the core pin is opened and closed. Preferably, the piston is movable between an open position and a closed position of the channel. Preferably, the chamber is opened and closed, the chamber is connected via a space between the chamber, the valve actuator and the core pin, and the piston is movable between an open position and a closed position of said channel, and the piston is movable between an open position and a closed position of said channel. is controlled by an actuator that is steered as a result of measuring the pressure level within the piston and the pressure level of the pressure source.

Preferably, the chamber is opened and closed, the chamber is connected via a space between the chamber, the valve actuator and the core pin, and the piston is movable between an open position and a closed position of said channel, and the piston is movable between an open position and a closed position of said channel. is controlled by an actuator that is steered as a result of a measurement of the pressure level of the pressure in the pressure source and the pressure of the pressure source.

Preferably, the wall of the container comprises an elastically deformable material comprising reinforcing means. Preferably, the reinforcing windings have a braid angle different from 54° 44'. Preferably, said reinforcing means comprises a textile reinforcement that allows expansion of said container when moving into a first longitudinal position and allows contraction when moving into a second longitudinal position. Preferably, the piston is manufactured by a production system having multiple vulcanization cavities. Preferably, the reinforcing means comprises fibers to enable expansion of the container when moving into the first longitudinal position and to allow contraction when moving into the second longitudinal position.

Preferably, the piston is manufactured by a production system with multiple vulcanization holes, the piston being attached to the cavity of the cap by rotating the fibers and the cabs at different speeds while the fibers are pressed inside the cap. Preferably, the fibers are arranged with respect to the trellis effect. Preferably, the reinforcing means comprises a flexible material arranged in the container, the reinforcing means comprising a plurality of at least substantially elastic support members rotatably fixed to a common member, the common member being connected to the skin of the container. Preferably, said members and/or the common member are expandable. Preferably, the pressure on the wall of the container is accumulated by a spring force actuator. Preferably, the piston comprises a reinforcing material arranged outside the container. Preferably, the container moves in a cylinder around a tapered wall. Preferably, the chamber is convex, and the operating force is tangent to the maximum force set during the stroke.

According to one embodiment of the present invention, there is provided a combination of a piston with any of the containers having bendable walls, the cross sections of the different cross sections having different cross sectional shapes, the change in the cross sectional shape of the chamber being at least substantially continuous between the first longitudinal position of the chamber and the second longitudinal position of the chamber, the piston being further designed to adapt itself and the sealing means to the different cross sectional shapes, the piston including a container having a production size close to the perimeter of the first longitudinal position of the chamber.

Preferably, the cross-sectional shape of the chamber at the first longitudinal position of the chamber is at least substantially circular, and the cross-sectional shape of the chamber at the second longitudinal position of the chamber is at least substantially circular.
It is elongated, such as an oval, and has a first dimension that is at least 3, preferably at least 4 times the first dimension at an angle to the first dimension.

Preferably, the cross-sectional shape of the chamber in its first longitudinal position is at least substantially circular, and the cross-sectional shape of the chamber in its second longitudinal position includes at least two or more, for example lobe-shaped parts. including. Preferably, the first circumferential length of the cross-sectional shape of the cylinder at the first longitudinal position is between 80 and 120 of the second circumferential length of the cross-sectional shape of the chamber at its second longitudinal position. %, such as 85-115%, preferably 90-110%, such as 95
-105%, preferably 98-102%. Preferably, the first and second circumferential lengths are at least substantially the same.

According to one embodiment of the present invention, there is provided a piston-chamber combination comprising an elongated chamber surrounded by an internal chamber wall and including a piston sealingly movable within the chamber, the piston being movable within the chamber at least from its second longitudinal position to its first longitudinal position, the chamber including an elastically deformable inner wall along at least a portion of the length of the chamber wall between the first longitudinal position and the second longitudinal position, the chamber having a first cross-sectional area at the first longitudinal position when the piston is positioned at that position that is greater than a second cross-sectional area at the second longitudinal position of the chamber when the piston is positioned at that position, the change in cross-section of the chamber being at least substantially continuous between the first longitudinal position and the second longitudinal position when the piston is moved between the first longitudinal position and the second longitudinal position. The piston-chamber combination includes an elastically expandable container having shapes that match each other during a piston stroke, a continuous seal, and a piston having its production size when positioned at the second longitudinal position of the chamber. Preferably, the piston is made of an at least substantially incompressible material. Preferably, the piston has a tapered shape in cross section along the longitudinal axis in a direction from a first longitudinal position to a second longitudinal position of the chamber. Preferably, the angle between the wall of the cylinder and the central axis is at least less than the angle between the tapered wall of the piston and the central axis of the chamber. Preferably, the chamber comprises an outer support structure surrounding said inner wall, and a fluid held by a space defined by said outer support structure and said inner wall. Preferably, the space defined by the outer structure and the expandable inner wall. Preferably, the piston comprises an elastically deformable container comprising a deformable material and designed according to Statements 7 to 17.

According to an embodiment of the invention, there is provided a pump for pumping fluid, said pump comprising: a combination according to any of the foregoing, means for engaging a piston from a position external to the chamber, connected to the chamber; and a fluid inlet including valve means and a fluid outlet connected to the chamber. Preferably, the engagement means has 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 of the chamber. Preferably, the engagement means has an outer position in which the piston is in the second longitudinal position of the chamber and an inner position in which the piston is in the first longitudinal position of the chamber.

According to one embodiment of the present invention there is provided a shock absorber comprising a combination according to any of statements 1 to 80 above and means for engaging the piston from a position outside the chamber, the engaging means having an outer position in which the piston is at the first longitudinal position of the chamber and an inner position in which the piston is at the second longitudinal position.

Preferably, the shock absorber comprises a fluid inlet connected to the chamber and comprises valve means. Preferably, the shock absorber further comprises a fluid outlet connected to the chamber and comprises valve means. Preferably, the chamber and the piston form an at least substantially sealed cavity containing a fluid, the fluid being compressed as the piston moves from the first longitudinal position of the chamber to the second longitudinal position. Ru. Preferably, the shock absorber further comprises means for biasing the piston into the first longitudinal position of the chamber.

According to an embodiment of the invention, the combination according to any of the foregoing 1 to 80, means for engaging the piston from a position external to the chamber, a first longitudinal position and a second longitudinal position of the chamber. An actuator is provided that includes means for introducing fluid into the chamber to move the piston between the chambers.

Preferably, the actuator further comprises a fluid inlet connected to the chamber and provided with valve means. Preferably, the actuator further includes a fluid outlet connected to the chamber and includes valve means. Preferably, the actuator further comprises means for biasing the piston into the first or second longitudinal position of the chamber. Preferably, the introducing means includes means for introducing pressurized fluid into the chamber. Preferably, said introducing means are arranged to introduce a flammable fluid, such as gasoline or diesel, into said chamber, and said actuator further comprises means for combusting said flammable fluid. Preferably, the introducing means is configured to introduce an inflatable fluid into the chamber, and the actuator further comprises means for inflating the inflatable fluid. Preferably, the actuator further comprises a crank configured to convert movement of the piston into rotation of the crank.

Preferably, the invention relates to a motor, the motor comprising a combination according to any of the preceding statements. Preferably, the motor comprises a combination according to any of the preceding statements, a power source and a power supply device. Preferably, the power unit is mobile.
653-2 SPECIFICALLY PREFERRED EMBODIMENTS According to one embodiment of the present invention, there is provided a piston-chamber combination comprising a container comprising an elongated chamber bounded by an internal chamber wall, a piston within the chamber, sealably movable relative to at least said chamber wall between a first longitudinal position and a second longitudinal position of the chamber, said chamber having a cross-section of different cross-sectional areas and different circumferential lengths at intermediate longitudinal positions between said first longitudinal position and said second longitudinal position, said cross-sectional area and circumferential length being at least substantially continuously different, said cross-sectional area and circumferential length at said second longitudinal position being smaller than said cross-sectional area and circumferential length at said first longitudinal position, said piston being elastically deformable thereby providing different cross-sectional areas and circumferential lengths of said piston. Adapting same to said different cross-sectional areas and different circumferential lengths of the chamber during relative movement of the piston between the first longitudinal position and the second longitudinal position through said intermediate longitudinal positions.
The chamber, the vessel, is expandable and elastically deformable to provide different cross-sectional areas and circumferential lengths, and the piston is in communication with a pressure source.

Preferably, the communication location is through a closed space, the closed space having a variable volume. Preferably, the communication location is through a valve. Preferably, the communication location is a pressure source in communication with the container by an outlet valve and an inlet valve. Preferably, the outlet valve, the expansion valve, is preferably a valve having a spring biased core pin, such as a Schrader valve, the core pin moving towards the pressure source when the valve is closed. Preferably, the inlet valve is an expansion valve, preferably a valve having a spring biased core pin, such as a Schrader valve, the core pin moving towards the container when the valve is closed.

According to an embodiment of the invention, a housing connected to a source of pressure medium, a coupling for receiving an actuated valve, and a first cylinder wall end surrounded by a cylinder wall of a predetermined cylinder wall diameter; a valve actuator for actuating a valve within a housing, the valve actuator having a second cylinder end distal to the first cylinder end; a piston fixedly connected to an actuation pin for engaging a spring-forced valve core pin of the valve and moving the piston to a first piston position at a first predetermined distance from the first cylinder end; a conduction channel for conducting pressure medium from the cylinder to the joint when the piston is moved to the second piston, and prohibiting conduction of pressure medium between the cylinder and the joint when the piston is moved to the second piston. A valve actuator is also provided. a position of the piston at a second distance from the first cylinder end at a second predetermined distance greater than the first distance, the conductive channel being disposed in the cylinder wall and at the predetermined distance; opening into said cylinder at a cylinder wall having a cylinder wall diameter, said piston having a piston ring having a sealing edge sealingly mating with said cylinder wall, whereby said second opening and closing a channel connecting a piston chamber and a space between a valve actuator and a core pin, blocking conduction of pressure medium into said channel at a position and opening said channel at said first position of said piston; It is preferable to be able to do so. Preferably, the channel connecting the chamber and the space between the valve actuator and the core pin can be opened and closed. Preferably, the piston is movable between an open position and a closed position of the channel. Preferably, the channel can be opened and closed, the channel is connected via a space between the chamber, the valve actuator and the core pin, and the piston is movable between an open position and a closed position of said channel; Movement of the piston is controlled by an actuator that is steered as a result of measuring the pressure level within the piston and the pressure level of the pressure source.

Preferably, the channel can be opened and closed, the channel being connected via the space of the chamber and the space between the valve actuator and the core pin, the piston being movable between an open position and a closed position of said channel, the movement of the piston being controlled by an actuator which is operated as a result of measuring the pressure level of the pressure in the piston and the pressure level of the pressure source. Preferably, said closed space comprises a first closed space. Preferably, said closed space comprises a second closed space. Preferably, the first closed space comprises a spring biased pressure tuned piston.

According to an embodiment of the invention, means are also provided for defining a volume of the first enclosed space, such that the pressure of the fluid within the first enclosed space is related to the pressure within the second enclosed space. do.
Preferably, the spring-loaded pressure-tuning piston is a check valve through which fluid from an external pressure source can flow into the first enclosed space. Preferably, the second valve is supplied from an external pressure source through a valve having a spring-loaded core pin, such as a Schrader valve, preferably an expansion valve.
Fluid flows into the closed space. Preferably, the circumferential length of the piston is approximately equal to the circumferential length of the chamber in the second longitudinal direction and is expandable from its manufactured size in a direction transverse to the second longitudinal direction; thereby, during the relative movement of the piston from said second longitudinal direction to said first longitudinal direction, in a stress-free and undeformed state, allowing expansion of the piston from its manufacturing size to its manufacturing size; A piston manufactured to have the manufacturing size of the container.

Preferably, the cross-sectional area of the chamber at its second longitudinal position is between 98% and 5% of the cross-sectional area of the chamber at its first longitudinal position. Preferably, the combination is such that 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. Preferably, the cross-sectional area of the chamber at the second longitudinal position is about 50% of the cross-sectional area of the chamber at the first longitudinal position. Preferably, the walls of the container include an elastically deformable material including reinforcing means. Preferably, the container includes a deformable material. Preferably it is a fluid or a mixture of fluids, such as water, steam and/or gas, or a foam deformable material.
507 SUMMARY OF THE INVENTION The valve actuator of the invention and its embodiments are the subject of claims 1 and 2 to 17, respectively. A valve connector and a pressure vessel or manual pump comprising a valve actuator according to the invention are the subject matter of claims 18 and 19, respectively. Claim 20 is directed to the use of the valve actuator in a fixed structure.

The present invention provides a valve actuator with a combination of an inexpensive cylinder with a piston moving to drive the actuation pin and an actuation pin having a simple structure. This combination can be used in fixed structures such as chemical plants where the actuation pin engages a spring-force actuated core pin of a valve (e.g., a release valve), as well as in valve connectors (e.g., for inflating vehicle tires). The shortcomings of conventional valve connectors are overcome by the valve actuator of the present invention. The valve actuator features a piston having a piston ring that fits into the cylinder, and in its first position, the piston is a first predetermined distance from a first end of the cylinder. In its second position, the piston is a second predetermined distance from the first end of the cylinder, the second predetermined distance being greater than the first predetermined distance. The cylinder wall is configured to prevent the piston from moving past the first end of the cylinder.
a conduction channel for allowing conduction of gas and/or liquid medium between the cylinder and the coupling when the piston is in a first position, and conduction of gas and/or liquid medium between the cylinder and the coupling is inhibited by the piston when the piston is in a second position.

An embodiment of the inventive valve actuator as defined in claim 6 features a conduction channel from the pressure source to the valve to be actuated, which comprises an enlargement of the cylinder diameter arranged around the piston of the actuation pin at the bottom of the cylinder when the piston is in a first position, allowing the medium to flow from the pressure source, e.g. from a Schrader valve, to the open spring-pressurized actuation valve core pin. The enlargement of the cylinder diameter may be uniform or the cylinder wall may have a 10 mm diameter enlargement near the bottom of the cylinder, where the distance between the centerline of the cylinder and the cylinder wall increases.
The piston may include a plurality of portions, which allows the gas and/or liquid medium to flow freely around the edge of the piston ring when the piston is in the first position. A variant of this embodiment has a valve actuator configuration whose cylinder has an expansion of twice its diameter. The distance between the expansions can be the same as the distance between the sealing levels of the sealing means. If three valves of different sizes can be combined, the valve actuator can comprise three enlarged cylinders. However, it is also possible to connect valves of different sizes to a valve actuator with a single configuration for expanding the diameter of the cylinder. Therefore, we now look at the number of expansions. It may differ from the number of different sizes of valves that can be combined.

Another embodiment of the invention, as set forth in claim 10, features a conductive channel through a portion of the body of the valve actuator. The channel forms a passage for the gas and/or liquid medium between the cylinder and the part of the valve actuator that is connected to the valve. The orifice of the channel opening in the cylinder is such that when the piston is in the first position, the pressurized gaseous and/or liquid medium flowing from the pressure source into the cylinder further passes through the channel to the actuated valve. arranged in a flowing manner. When the piston is in the second position, it blocks the cylinder, making it impossible for pressurized gas and/or liquid medium to flow into the channel.

Instead of air, any type of gas and/or liquid (mixture) can actuate the actuating pin and flow around the piston of the valve actuator when the piston is in its first position. The invention can be used for all types of valve connectors that can couple valves with spring-actuated core pins (e.g. Schrader valves), regardless of the coupling method or number of coupling holes of the connector. Furthermore, the valve actuator can be coupled to, for example, a foot pump, a car pump, or a compressor. The valve actuator can also be integrated into any pressure source (e.g. a hand pump or a pressure vessel), regardless of the availability of fastening means in the valve connector. The invention can also be used for permanent constructions where the actuator pin of the actuator engages with the core pin of a permanently attached valve.
507 SPECIFICALLY PREFERRED EMBODIMENTS According to one embodiment of the present invention there is provided a valve actuator for operation with a valve having a spring-actuated valve core pin, the valve actuator comprising a housing connected to a pressure medium source, said housing including a coupling for receiving a valve to be actuated therein, a cylinder surrounded by a cylinder wall of a predetermined cylinder wall diameter and having a first cylinder wall end and a second cylinder end remote from said first cylinder end, a piston movably disposed within said cylinder and fixedly coupled to an actuation pin for engaging said spring-actuated valve core pin of a valve received within said coupling, said piston being adapted to actuate said valve core pin.
a conducting channel for conducting pressure medium from the cylinder to the coupling when the piston is moved to a first piston position at the first predetermined distance from a first cylinder end, and when the piston is moved to a second piston position, the conducting channel is disposed in the cylinder wall and opens into the cylinder at a cylinder wall portion having the predetermined cylinder wall diameter at a second predetermined distance, the second distance being greater than the first distance, the piston comprising a piston ring having a sealing edge that sealingly fits against the cylinder wall, thereby preventing the conduction of pressure medium into the channel at the second position of the piston and opening the channel at the first position of the piston.

Preferably, said first predetermined distance is greater than zero. Preferably, said first predetermined distance is approximately zero. Preferably, a stopper is provided to limit movement of the piston in the first piston position. Preferably, a tapered portion at the first end of the cylinder and a conical portion of the piston are configured to coincide with said tapered portion when the piston is in the first piston position.

Preferably, the conducting channel is formed by an enlargement of the diameter of the cylinder wall arranged radially around the piston so that the pressure medium can flow freely around the edge of the piston ring when the piston is in its first piston position. Preferably, the conducting channel is an enlargement of the cylinder diameter formed on one or more parts of the circumference of the cylinder wall.

Preferably, the expansion wall comprises a cylindrical expansion wall section and an inclined expansion wall section, the cylindrical axis forming an angle greater than 0° and smaller than 20°, the inclined expansion wall section being located between the cylindrical expansion wall section and a cylinder wall section having a predetermined cylindrical wall diameter. Preferably, the channel section of the conductive channel between the cylindrical expansion wall section and the coupling section is designed as a tapered channel section formed as a groove or as a hole (107) parallel to the central axis of the cylinder.

Preferably, a coupling is connected by the electrically conductive channel to an orifice in the cylinder wall, the orifice being a connection between the piston and the second end of the cylinder when the piston is in the first piston position. located at a distance from the first cylinder end such that the orifice is located therebetween.

Preferably, the piston is movable within the cylinder to a third position and a fourth position corresponding to a third predetermined distance and a fourth predetermined distance, respectively, from the first end of the cylinder. the third predetermined distance is greater than the second predetermined distance; the fourth predetermined distance is greater than the third predetermined distance; enabling conduction of a gas and/or liquid medium between the cylinder and the coupling when the piston is in the fourth position; A second channel is provided that prevents the conduction of gas and/or liquid media.

Preferably, the coupling for sealing a valve actuator on valves of various types and/or sizes comprises an embodiment for sealing a valve actuator within the sealing means, the sealing means comprising a first annular sealing member. and is placed coaxially with the central axis of the joint,
a second annular portion displaced in the direction of the central axis of the coupling portion, the first annular portion being closer to the opening of the coupling portion than the second annular portion; is larger than the diameter of the second annular portion. Preferably, an embodiment is provided with a fixing screw in the coupling part for fixing the valve actuator to the expansion valve.

Preferably, said fixing screw is a temporary fixing screw. Preferably, the cylinder wall comprises:
The cylinder sleeve is formed as a cylinder sleeve, which is clamped and sealed in the housing, and is formed with said inclined enlarged wall portion, said cylinder wall being angled with the wall portion away from the first cylinder end such that the piston ring is not sealed therein. Preferably, said cylinder sleeve is fixed and sealed to the wall of the housing by a snap lock. In a preferred embodiment, a sealing means is provided in the coupling for sealing the valve actuator onto a valve having a spring-loaded valve core pin.

According to an embodiment of the invention, there is provided a valve connector coupled to a hand pump, foot pump, vehicle pump, pressure vessel or compressor for inflating a vehicle tire, as claimed in any of claims 1 to 16. valve actuator.

There is also provided, in accordance with one embodiment of the present invention, a pressure vessel or hand pump for inflating vehicle tires, where an integrated valve actuator is provided.
According to one embodiment of the present invention, there is also provided a valve actuator for a fixed structure, such as a chemical plant.
19597 SUMMARY OF THEINVENTION In a first aspect, the present invention relates to a piston and chamber combination comprising an elongated chamber bounded by an internal chamber wall, a piston within the chamber sealingly movable relative to said chamber wall at least between a first longitudinal position and a second longitudinal position of the chamber, said combination engaging a rigid surface to enable said movement, wherein said combination is movable relative to said surface.

The provider of force for enabling relative movement of the parts of the combination may itself move, and the last mentioned path of movement is the path of relative movement of the piston rod, piston and chamber. does not match exactly. Therefore, the force provider and combination system can provide flexibility somewhere within the system to avoid damage. To enable said relative movement, if the force supplier is able to engage the combination with a varying force and also hold the non-moving part of the combination towards the surface of the rigid body, There may be conflicting requirements for combinations. However, this is limited to cases where the surface of the rigid body also has the function of providing a reaction force to the combination. The last mentioned can occur when the pump engages the human body, during which the pump is pushed by the user's foot to a rigid surface, such as the floor, for example. Especially if the floor is not level, especially if someone standing is using a floor pump to pump out the tires. Therefore, this combination should be movable relative to the rigid surface in order to follow the path of the force provider.

In a second aspect, the problem of incompatibility is particularly important when the chamber is used with different cross-sectional areas at the first and second longitudinal positions, and with at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at the second longitudinal position being smaller than the cross-sectional area at the first longitudinal position. This is also valid when the cross-sectional areas at the first and second longitudinal positions are different in size, but have equal circumferential sizes at the first and second longitudinal positions.

In an optimized embodiment to obtain the highest level of energy reduction, the chamber of a floor pump for tire inflation, for example, has the smallest possible cross-sectional area at its bottom and the largest cross-sectional area at its top. has. Therefore, at the smallest cross-sectional area, there is a maximum force moment that engages the transition from the chamber to the base of the pump. Therefore, this combination should be movable relative to the rigid surface in order to follow the path of the force provider.

In a third aspect, the combination includes a base for engaging the combination with a rigid surface and allowing relative movement of the piston and the chamber, the combination being rigidly fixed to the base, the base comprising: Can move relative to a rigid surface.

The base may have three engagement surfaces on the rigid surface, ensuring stable positioning of the combination even if the rigid surface is not flat. This combination can then wrap any line between two of the three engagement surfaces. However, this is an insufficient solution since the human resource supplier path is usually a three-dimensional path. Also, this solution does not provide compensation for the positioning of combinations when the surface is not horizontal. Additionally, in the case of floor pumps for tire inflation, movement can typically be inhibited when the user pushes the base of the pump toward a hard surface.

In a fourth aspect, the combination comprises a base for engaging the combination to a rigid surface and allowing relative movement of the piston and the chamber, and the combination comprises a base for engaging the combination to a rigid surface and allowing relative movement of the piston and the chamber, the combination is fixed flexibly.

This solution, combined with a foundation with three engagement surfaces, is an optimized solution that fits all requirements. That is, the combined path can be any path used by the force provider (e.g. the user), while the base is restrained, for example, by the user's foot, standing on a surface. Not only can it compensate for a level, but also a rigid surface, but not the base, so that the combination is still vertical water, the user of the floor pump can start any path during the stroke. After use, the combination automatically returns 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 is provided at the end of the cylinder, held in a ball bar ring in the base. The ball may be combined with a spring, which limits the deflection of the combination and returns it to its default after use. This solution (not shown) is more expensive than a bushing.

This is also valid for equal piston-chamber combinations of different cross-sectional areas and different periodic sizes. The guide means may comprise a washer having a small hole with a suitable fit with the piston rod, the washer being movable within the large hole in the cap, the piston rod being primarily lateral to the combination. It is possible to move in the direction. The washer can be returned to its default position by a spring force, for example an O-ring between the hole in the cab and the outside of the guide means.

The size of the aforementioned holes, together with how much the piston structure allows the piston rod, determines the degree of deflection of the piston rod. If the piston rod is firmly fixed to the piston, the structure 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 determined only by the guiding means.

In a ninth embodiment, the contact surface of the guiding means may be a circular line, for example by a convex cross-sectional inner wall of the hole of the guiding means, in order to allow deflection of the piston rod relative to the central longitudinal axis of the remainder of the assembly.

In a tenth aspect, the piston may be rounded to accommodate movement of the piston rod, or the connection of the piston to the piston rod may be flexible and rotatable.
In an eleventh aspect, the invention relates to a piston and chamber combination. The centerline of the handle portion located opposite the central axis of the combination has an angle different from 180°.
The centerline of the user's hand when operating the pump handle has different positions depending on how the handle is held in the hand.

In the case of classic floor pumps, high acting forces can occur in a circular cross-section cylinder of a certain size. If a relatively strong force is transmitted from the user's arm through the hand connected to this arm, the hand is best positioned relative to the arm when no moment of force occurs. This is obtained if the longitudinal axis of the arm passes through the center point of the axis of the part of the handle, which is gripped by the handle and connected to the arm.

Due to the relative magnitude of the forces, the grip of the hand on the handle should be firm. This can be done by the curve of the hand, such as an open grip, where the grip design can include a section with a circular cross section. The size of the section can be varied depending on the distance to the central axis of the piston-chamber combination.

A preferred angle between the portions of the handle may be 180° in a plane perpendicular to the central axis of the piston-chamber combination. However, it may be different from 180°. Furthermore, the angle may be less than 180° in a plane containing the central axis. To avoid slipping of the hand from these projections, stops can be provided. They can also be used to transmit force. Of course, there are other options, 180° and beyond 180°.

In the case of an innovative floor pump having a chamber with a cross-section of various sizes between two positions of the chamber in the longitudinal direction, the force may be small. The hand is positioned relative to the arm such that when a relatively low force is transmitted from the user's arm through the hand connected to said arm, a constant force moment occurs. The contact area is the area of the open hand. The handle may be designed to have a cross-section bounded by a curve, for example an ellipse. An axis perpendicular to the central axis of the piston-chamber combination may be larger than an axis parallel to said axis.

The preferred angle between the two parts of the handle in the plane perpendicular to the central axis of the piston-chamber combination may be less than the bit (best!) than 180°. These positions of the handle parts follow the position of the rest of the hand. Both positions can be obtained by one handle design if the handle can rotate about the central axis of the piston-chamber combination.

In order to avoid the presence of moments of force, a line passing through the centers of both parts of the handle in a plane perpendicular to the central axis of the piston-chamber combination cuts the last mentioned axis. In the plane containing the central axis of the piston-chamber combination, the angle may be less than or equal to 180°, or may be different.

A conical cylinder can significantly reduce the size of the working force. The special arrangement creates a conical cylinder shape in the longitudinal direction of the chamber, which is formed so that the force on the handle remains constant during the stroke. This force is caused by the fact that the valve piston is attached to the valve seed when the valve opens late, or by the fact that there is dynamic friction due to the small cross-sectional size of the channel, i.e. the chamber may be modified by forces originating from sources other than the shape of the . Additionally, the friction of the piston against the chamber walls may change during the stroke due to changes in the size of the contact area. The shape of the cylinder shown longitudinally in all relevant drawings of this patent application was created in the above manner while the cross-section of the conical cylinder is circular, which is also shown in the relevant drawings. ing. The shape limit is the minimum size of the piston.

The present invention therefore also relates to a pump for pumping a fluid, the pump comprising a combination according to any of the above aspects, means for engaging the piston from a position outside the chamber, a fluid inlet connected to the chamber and comprising valve means, and a fluid outlet connected to the chamber.

In one situation, the engagement means can have an outer position where the piston is in its first longitudinal position and an inner position where the piston is in its second longitudinal position. This type of pump is preferred where pressurized fluid is desired.

In another situation, the engagement means may have an outer position with the piston in its second longitudinal position and an inner position with the piston in its first longitudinal position. This type of pump is preferred when no substantial pressure is desired, but simply to transport fluid.

In a situation where the pump is configured to stand on a floor and the piston/engagement means is configured to forcefully compress a fluid such as air downwards, the maximum force may economically be applied at the lowest position of the piston/engagement means/handle. Thus, in the first situation, this means that the highest pressure is applied there. In the second situation, this simply means that the largest area, and therefore the largest volume, is found at the lowest position. However, due to the fact that a pressure in excess of the pressure in the tire is required to open the valve of the tire, for example, a minimum cross-sectional area may be desired just before the lowest position of the engagement means in order for the resulting pressure to open the valve and a larger cross-sectional area to force the fluid into the tire (see FIG. 2B).

The present invention also relates to a shock absorber. The shock absorber is a combination according to any of the combination aspects, means for engaging the piston from a position outside the chamber, said engaging means being in a first longitudinal position of the piston. Means is provided having an outer position and an inner position in which the piston is in its second longitudinal position. The absorbent body further includes a fluid inlet connected to the chamber and may include valve means. The absorbent body may also include a fluid outlet connected to the chamber and may include valve means. Preferably, the chamber and the piston form an at least substantially sealed cavity containing a fluid, which fluid is compressed as the piston moves from the first longitudinal position to the second longitudinal position. Typically, the absorber includes means for biasing the piston towards the first longitudinal position.

Finally, the invention relates to an actuator. The actuator combines according to any of the combination aspects, means for engaging the piston from a position outside the chamber, for displacing the piston between a first longitudinal position and a second longitudinal position. Means for introducing fluid into the chamber is provided. The actuator may include a fluid inlet connected to the chamber and provided with valve means. A fluid outlet may also be provided connected to the chamber and including valve means. Additionally, the actuator may include means for biasing the piston into the first or second longitudinal position.
19597-1 Particularly Preferred Embodiments According to one embodiment of the present invention, comprising an elongate chamber bounded by an internal chamber wall, at least a first longitudinal position of the chamber and a second longitudinal position of the chamber are provided. a piston sealably movable with respect to said chamber wall between longitudinal positions, said combination flexibly secured to a base for engaging a rigid surface, said combination resiliently A piston-chamber combination is provided which is flexibly fixed to said base by a flexible bushing.

Preferably, it is a resiliently flexible bushing mounted in a hole in the base, and the cylinder mounted in the hole in the bushing. Preferably, the bushing includes a groove for cooperating with a corresponding protrusion on the cylinder. Preferably, the bushing includes a protrusion for cooperating with a corresponding groove on the cylinder. Preferably, the bushing includes a protrusion connected to the top of the base. Preferably, the wall thickness of the bushing is greater than the wall thickness of the chamber. Preferably, it includes three engagement surfaces for engaging the rigid surface.

Preferably, the piston means has chamber cross-sections of different cross-sectional areas and different circumferential lengths at a first longitudinal position and at a second longitudinal position, the cross-sectional area and circumferential length being successively different at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than said cross-sectional area and circumferential length at said first longitudinal position, and the piston means is operable to vary its dimensions so as to adapt the different cross-sectional areas and circumferential lengths of the chamber to the different cross-sectional areas and different circumferential lengths of the chamber during relative movement of the piston means between the first and second longitudinal positions through said intermediate longitudinal positions of the chamber.

Preferably, the piston has a chamber cross-section of different cross-sectional areas and equal circumferential lengths at the first and second longitudinal positions, and has a continuously different cross-sectional area and circumferential length at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at the second longitudinal position being smaller than the cross-sectional area and circumferential length at the first longitudinal position, and the piston can be varied in size during relative movement of the piston means through the intermediate longitudinal positions of the chamber by providing different cross-sectional areas and circumferential lengths of the piston corresponding to the different cross-sectional areas and equal circumferential lengths of the chamber.

Preferably, the pump comprises a piston and chamber combination, comprising means for engaging the piston from a position external to the chamber, and a fluid outlet and a fluid inlet including valve means connected to the chamber. be.

Preferably, the shock absorber is a piston and chamber combination comprising means for engaging the piston from a position outside the chamber, the engagement means having an outer position where the piston is at a first longitudinal position of the chamber and an inner position where the piston is at a second longitudinal position, the chamber and piston forming a sealed cavity containing a fluid that is compressed when the piston moves from the first longitudinal position to the second longitudinal position.

Preferably, the piston-chamber combination includes means for engaging the piston from a position outside the chamber and means within the chamber for displacing the piston between a first longitudinal position and a second longitudinal position. and means for introducing fluid.
19597-2 Particularly Preferred Embodiments According to one embodiment of the invention, the invention comprises an elongated chamber bounded by an internal chamber wall, and piston means within the chamber, the piston means being arranged in at least a first portion of the chamber. sealingly movable relative to the chamber wall between a longitudinal position and a second longitudinal position, the combination engaging a rigid surface, the combination penetrating a cap overlying the cap. and a piston rod providing a piston-chamber combination guided by guiding means movably connected to the cap.

Preferably, the guide means is a washer with an aperture around the piston rod, the washer being held in the cap between two surfaces, and a flexible O-ring being held in the cap in a space between the surfaces and the guide means, the cross-sectional area of the space being greater than the cross-sectional area of the O-ring.

Preferably, the guide means includes a convex guide surface that guides the piston rod. Preferably it is a rounded piston at the connection with the wall of the chamber. Preferably, the connection between the piston rod and the piston (44) is flexible. Preferably, the piston-chamber combination is a pump comprising means for engaging the piston from a position outside the chamber, and a fluid outlet and a fluid inlet including valve means are connected to the chamber. Preferably, the piston and chamber combination comprises means for engaging the piston from a position external to the chamber, the engaging means being arranged in a position external to the chamber in which the piston is in a first longitudinal position. , an inner position where the piston is in a second longitudinal position, the chamber and the piston containing fluid that is compressed when the piston moves from the first longitudinal position to the second longitudinal position. It is a shock absorber that forms a sealed cavity. Preferably, the piston-chamber combination includes means for engaging the piston from a position outside the chamber and means within the chamber for displacing the piston between a first longitudinal position and a second longitudinal position. and means for introducing fluid.

Preferably, the chamber has cross-sectional areas of different cross-sectional areas and different circumferential lengths at the first and second longitudinal positions, and the cross-sectional area and circumferential length at an intermediate longitudinal position between the first and second longitudinal positions, the second longitudinal position are continuously different, and the cross-sectional area and circumferential length at the second longitudinal position are different.

The piston means has a cross-sectional area and circumferential length smaller than at the first longitudinal position, and the piston means is capable of varying dimensions to accommodate different cross-sectional areas and different circumferential lengths of the chamber during relative movement of the piston means between the first longitudinal position and the second longitudinal position through the intermediate longitudinal position of the chamber.

Preferably, the piston has chamber cross-sections of different cross-sectional areas and equal circumferential lengths at first and second longitudinal positions, and at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longitudinal position, and said piston is variable in size by providing different cross-sectional areas and circumferential lengths of said piston to accommodate said different cross-sectional areas and circumferential lengths of said piston during relative movement of said piston means between said longitudinal positions and said second longitudinal positions through said intermediate longitudinal positions of said chamber.

Figure 1A shows a longitudinal cross-section of a chamber with fixed and distinct regions of cross-section, a first embodiment of a piston including a woven reinforcement that varies radially and axially in size during the stroke, the piston arrangement is shown first pressurized, at the end of the stroke, where the piston is unpressurized to its production size, and Figure 1B is an enlarged view of the piston of Figure 1A at the start of the stroke. FIG. 1C is an enlarged view of the piston of FIG. 1(A) at the end of the stroke. Figure 2A shows a second embodiment of a piston including a longitudinal section of the chamber with fixed and distinct areas of cross section and a fiber reinforcement with radially and axially varying dimensions of the elastic material of the wall during the stroke (trellis effect). In this case, the piston arrangement is shown initially and, at the end of the stroke, pressurized. Here, the piston is unpressurized to its production size.

FIG. 2B shows a close-up of the piston of FIG. 2A at the beginning of the stroke.
FIG. 2C shows a close-up of the piston of FIG. 2A at the end of the stroke. FIG. 3A shows a third embodiment of a piston including a longitudinal cross section of a chamber with fixed distinct areas of cross section and fiber reinforcement that varies radially and axially in dimension during the stroke (without a “trellis effect”).

The sequence is shown first and last where it has a production scale.
FIG. 3B is a close-up view of the piston of FIG. 3A at the beginning of a stroke.
FIG. 3C is a close-up view of the piston of FIG. 3A at the end of the stroke. FIG. 3D shows a top view of the piston of FIG. 3A, showing the left side: first vertical position, and the right side: second vertical position, reinforced by a planar wall passing through the central axis of the piston.

Figure 3E shows a top view of the piston of Figure 3A, with the skin partially passing through the central axis and partly outside the central axis - left side: first longitudinal position, right side: second longitudinal position; Reinforced in directional position.
FIG. 3F shows a top and plan view of a piston of another embodiment. Figure 4 shows a non-moving expansible piston in a chamber with walls parallel to the axis, but there is no pressure difference in the chamber on either side of the piston. Figure 5A shows the piston of Figure 4 in a momentary motionless state in a chamber with conical walls where the piston begins to expand, i.e. the movable cab moves towards the immovable cab. It is in a state of being Figure 5B shows the piston of Figure 5A being momentarily immobile and thereby expanding, i.e. movable, such that the contact area of the piston wall with the chamber wall increases at the second longitudinal position of said contact area. FIG. 3 is a diagram showing that the cab is immobile. Figure 5C shows that the contact area of the piston wall with the chamber wall increases at a first longitudinal position of said contact area, while the contact area of the piston wall with the chamber wall increases at a second longitudinal position of said contact area. FIG. 5B is a diagram showing the piston of FIG. 5B momentarily stationary and thereby expanding so as to decrease in directional position; the movable cab is stationary; FIG. 5D shows the piston of FIG. 5C, where the non-movable cap momentarily begins to move from the second longitudinal position to the first longitudinal position, thereby moving the piston in the same direction. FIG. 5E shows the piston of FIG. 5D, where piston movement is reduced due to increased contact area. Figure 6A shows an expandable piston moving within a closed conical chamber. FIG. 6B shows an expandable piston moving within a closed conical chamber where the chambers on both sides of the piston are in communication with the surrounding atmosphere. FIG. 6C shows an expandable piston moving within a closed conical chamber, where the chambers on both sides of the piston communicate with each other via a closed channel outside the chamber. FIG. 6D shows an expandable piston moving in a closed conical chamber, where the chambers on both sides of the piston communicate with each other via a closed channel inside the piston. FIG. 6E shows an expandable piston moving in a closed conical chamber where the chambers on both sides of the piston communicate with each other via a. Channels between the chamber wall and the piston wall FIG. 6F shows the expandable piston of FIG. 6E with a duct at the interface between the piston wall and the chamber wall. FIG. 6G shows a cross-sectional view of the piston rod of FIG. 6F and a view on the actuator piston from a first longitudinal position. FIG. 7A shows an enlargement of the piston of FIG. 1A at the end of the stroke when it is pressurized but does not move because the walls are parallel to the central axis. FIG. 7B shows the piston of FIG. 7A at a point where the center of the piston wall has a positive angle with respect to the central axis such that the container moves toward the first position. FIG. 7D is a three-dimensional view of a reinforcing matrix of elastic fiber material placed on the wall of the container when the container is inflated, and FIG. 7E shows the pattern of FIG. 6D when the wall of the container is inflated. Figure 7F shows a three-dimensional view of the reinforcing pattern of inelastic fibrous material placed on the wall of the container when inflating the piston. FIG. 7G is an enlarged view of the reinforcement matrix of FIG. 7F. Figure 8 shows a combination where the piston is moving within the chamber and around the tapered wall. FIG. 9A shows a fourth embodiment of a piston with a longitudinal section of the chamber with fixed different regions of cross-section and with an "octopus" device, limiting the extension of the container wall by the tentacles, which may be inflatable shows. The arrangement of the piston is shown first and shows the case where the piston has its production size at the end of the stroke. FIG. 9B shows an enlargement of the piston of FIG. 9A at the beginning of the stroke. FIG. 9C shows an enlargement of the piston of FIG. 9A at the end of its stroke. FIG. 9D shows the piston of FIG. 9A just before entering the cone of the chamber. Figure 10A shows that the pressurized oval piston moves from the second longitudinal position to the first longitudinal position, expanding the internal volume of the piston, thereby decreasing the internal pressure of the piston, and changing the shape of the piston. The dashed lines at both ends of the chamber indicate the outer contour of said piston with walls parallel to the central axis of the chamber, which can be turned into a sphere, compared to the case where the same size of the piston in Figure 10B results in an intermediate The size of the piston is shown, thereby indicating that the piston of FIG. 10B may be engaged and connected to the wall of the chamber, whereas FIG. 10A shows that it is connected in a sealed manner. Figure 10B shows the piston-chamber combination of Figure 10A, where the internal pressure of the piston increases the volume of the enclosed space either at the furthest first longitudinal position or back to the second longitudinal position. This is further reduced by varying the size of the piston, thereby continuously adapting it to the size of the chamber, in order to avoid jamming. Figure 10C shows a piston-chamber combination as in Figure 10, but the internal pressure of the piston returns from the confined space either at the furthest first longitudinal position or at the second longitudinal position. By removing fluid in between, or by reducing the internal pressure of the piston, the size of the piston is changed and continuously adapted to the size of the chamber to avoid jamming. FIG. 10D shows the process of FIG. 10A when the piston is spherical and is produced in a second longitudinal position. FIG. 10E shows the process of FIG. 10B when the piston is spherical and is produced in a second longitudinal position. FIG. 10F shows the process of FIG. 10C when the piston is spherical and is produced in a second longitudinal position. Figure 10G shows the process of Figure 10A. However, the size of the enclosed space decreases during movement from the second longitudinal direction to the first longitudinal direction. Position with reduced use of pressurized medium per stroke Figure 10H shows a similar process of Figure 10B. Figure 10I shows a similar process to Figure 10C. Figure 10J shows the process of Figure 10D. The exception is that during the movement from the second longitudinal position to the first longitudinal position, the size of the enclosed space is reduced and the amount of pressurized medium used per stroke is reduced. Figure 10K shows a similar process to Figure 10E. Figure 10L shows a similar process to Figure 10F. FIG. 10M is a schematic diagram of the motor configured in FIGS. 12A and 12C. Having a propulsion system comprising an expandable actuator piston rotating in a circular chamber having a circular central axis about the center of the central axis of the motor. FIG. 10N schematically depicts the motor of FIGS. 13A, 13B with a propulsion system comprising (for example) five non-moving inflatable actuator pistons, said chamber being in a rotating circular chamber, said chamber being , having four sub-chambers concentric with the center of rotation and continuous with each other, having different transition cross-sectional areas and circumferences, said chambers rotating around a main axis through the center of said axis; ing. Consumption Technology Figure 11A schematically shows a motor with a propulsion system comprising an inflatable actuator piston and a two-stage piston pumping system, the two-stage piston pumping system comprising: It has the smallest pump and starter motor, located in an elongated chamber with successively different cross-sectional areas and circumferences, assembled on the crankshaft-axle and the pressure storage vessel, and in particular energized by solar energy. FIG. 11B schematically shows the control means and pressure management for the motor of FIG. 11A. FIG. 11C shows the mechanical assembly of the motor of FIG. 11A. 11B Main cylinder is not moving FIG. 11D shows pressure management of the expandable actuator piston on the crankshaft and connecting rod joint as shown in FIG. 11C. FIG. 11E shows details of the piston rod and connecting rod joint shown in FIG. 11C. Figure 11F shows details of the crankshaft suspension, and Figure 11F shows the channels in the crankshaft. 11A and 11B. Confined Space Volume Techniques FIG. 11G shows an alternative method of managing pressure changes in an expandable actuator piston by varying the volume of a confined space through the piston of a second piston-chamber combination; a third piston-chamber for managing the speed/output of the motor without constant compression of the pressure reservoir to pressurize the two-way actuator for changes in volume of the confined space; With additional adjustment of pressure through the combination piston. FIG. 11H shows the configuration of FIG. 11G, where constant recompression of the pressure storage vessel is performed, for example, by a cascade of pumps as shown in FIG. 11G. Figure 11A Figure 11I shows a partially assembled one cylinder motor based on the concept shown in Figure 11H where a speed controller and an ESVT pump are present. Powered by a two-way actuator powered by a battery, the pump for repressurizing the pressure storage vessel is powered by a separate electric motor powered by a battery, with each power line clearly marked. ing. Auxiliary power sources are shown in Figures 15A, B, C, E, F, at least one of which can charge the battery. Figure 11J shows a two-cylinder motor partially assembled based on Figure 11I, where each actuator piston-chamber combination has a separate speed controller and ESVT pump, and the speed controllers are connected to each other. It's communicating. The left side of Figure 11J shows a scale-up of the left part of Figure 11J. Figure 11J right shows a scale-up of the right part of Figure 11J. Figure 11K shows a partially molded one cylinder motor based on the concept shown in Figure 11H, where the actuator piston's ESVT pump is currently powered by the crankshaft and the last The one described above is powered by an electric motor powered by a battery. The speed controller (2-way actuator) is according to the one in Figure 11H, the pump for recompressing the pressure storage vessel is powered by a separate electric motor powered by a battery, and the auxiliary power source is According to Figures 15A, B, C, E, F, at least one of them can charge the battery. Figure 11L shows a partially machined two cylinder motor based on Figure 11K. ESVT pumps use one crankshaft, one for each actuator and piston combination. One speed controller for each actuator piston is in communication with each other, the pump for repressurizing the pressure reservoir is powered by a separate electric motor powered by a battery, and the auxiliary power source is Follow the diagram. 15A, B, C, E, F, at least one of which is capable of charging said battery. The left side of Figure 11L shows a scale-up of the left part of Figure 11L. Figure 11L right shows a scale-up of the right part of Figure 11L. FIG. 11M shows one cylinder motor partially assembled based on the concept shown in FIG. 11H. Here, the ESVT pump for the actuator piston chamber combination is powered by a camshaft, said camshaft is driven by an electric motor powered by a battery, and the speed controller is a two-way actuator in communication with the speeder. be. The pump for recompressing the pressure storage vessel is powered by a separate electric motor powered by a battery, and the auxiliary power source is shown in FIGS. 15A, B, C, E, F, and At least one of them can charge the battery. Figure 11N shows the two cylinder motors partially assembled according to Figure 11M. That is, one camshaft is used for the ESVT pump, one for each actuator piston-chamber combination. One speed controller for each actuator piston is in communication with each other, the pump for repressurizing the pressure reservoir is powered by a separate electric motor powered by a battery, and the auxiliary power source is Follow 15A, B, C, E, F. At least one of Figures 15A, B, E, F can charge the battery. The left side of Figure 11N shows a scale-up of the left part of Figure 11N. Figure 11N right shows a scale-up of the right part of Figure 11N. Figure 11o shows a partially molded one cylinder motor based on the concept shown in Figure 11K, where the actuator piston-chamber ESVT pump is a gas (e.g. air) cooled combustion motor. H2, driven by a crankshaft directly driven by auxiliary power from the battery, is used to perform the battery-powered electrolysis. The pump that repressurizes the pressure storage vessel is additionally driven directly by the combustion motor. The speed controller is driven by a two-way actuator that is powered by a battery. The battery according to Figure 15D is being charged by an alternator attached to the main motor shaft. The heat generated by the combustion motor can be used, for example, to warm up the interior of the vehicle. Figure 11P shows the two cylinder motors partially assembled based on Figure 11o, with one ESVT pump for each actuator piston-chamber combination directly powered by auxiliary power from the forced liquid-cooled combustion motor. It is driven by a driven crankshaft, which is guided by electrolysis of H2, with H2 powered by a battery. The pump that repressurizes the pressure storage vessel is driven directly by the combustion motor. One speed controller for each actuator piston-chamber combination is driven by a two-way actuator, communicates with each other, and is powered by a battery. The battery according to Figure 15D is charged by an alternator attached to the main motor shaft. The heat generated by the combustion motor can be used, for example, to warm up the interior of the vehicle. The left side of Figure 11P shows a scale-up of the left part of Figure 11P. Figure 11P right shows a scale-up of the right part of Figure 11P. Figure 11Q shows a partially molded one cylinder motor based on the concept shown in Figure 11K, where the actuator and chamber combination ESVT pump is powered by forced gas (e.g., air) cooled combustion. It is driven by a camshaft driven directly by auxiliary power from a motor and powered by a battery using H2 derived by electrolysis of H2O. The pump repressurizing the pressure storage vessel is driven directly by the combustion motor, the speed controller is driven by a two-way actuator driven by a battery, the battery according to Figure 15D is driven by an alternator mounted on the main motor shaft. It is charged. The heat generated by the combustion motor can be used, for example, to warm up the interior of the vehicle. Figure 11R shows the two cylinder motors partially assembled based on Figure 11Q, and one of the piston-chamber combinations of each actuator, the ESVT pump, is powered by a camshaft, and this camshaft uses H2 derived by electrolysis of H2O, driven directly by auxiliary power from a gas (e.g., air) forced-cooled combustion motor, said electrolysis being powered by a battery, and pressure storage. The pump repressurizing the vessel is driven directly by the combustion motor, and one of the piston-chamber combinations of each actuator is powered by a two-way actuator, in communication with each other and powered by a battery, FIG. 15D The battery is charged by an alternator attached to the main motor shaft. The heat generated by the combustion motor can be used, for example, to warm up the interior of the vehicle. Figure 11R left shows a scale-up of the left part of Figure 11R. FIG. 11R shows an enlarged view of the right portion of FIG. 11R. Figure 11S shows details of the joint at the base of the piston-chamber combination. 1061 in Figures 11I-11R with the main shaft of the motor.

FIG. 11T is a diagram showing details of the joint between the connecting rod of the actuator piston and the crankshaft on the motor main shaft according to FIGS. 11I to 11R.
Figure 11U shows details of the joint at the base of the piston-chamber combination. 1060 in Figures 11I-11R with the main shaft of the motor.

FIG. 11V shows the mechanism for driving the pump of FIGS. 11H-11R and its base.
FIG. 11W is a diagram showing a connection joint between the crankshafts of the two cylinder motors of FIGS. 11J, 11L, 11N, 11P, and 11R. FIG. 11W1 shows an improved seal between the crankshafts of FIG. 11W. Fig. 11X shows a connection joint between two crankshafts of a two-cylinder motor, with separate channels for each crankshaft. Fig. 11X' shows an improved seal between the crankshafts of Fig. 11X. Consumption Technology Figure 12A shows a schematic diagram of a motor having a propulsion system with an expandable actuator piston rotating in a circular chamber and a two-step piston pumping system in an elongated chamber with different transition cross-sectional areas and circumferences, and an electric starter motor assembled to a crankshaft axle and a pressure storage vessel, with a minimum pump and starter motor powered by solar energy including a control means. Fig. 12B shows a schematic of the control means and pressure management for the motor of Fig. 12B. The motor of Fig. 12A has a propulsion system with an expandable actuator piston moving in a non-moving chamber, with a center of rotation arranged concentrically and having four sub-chambers successive to each other, with different transition cross-sectional areas and perimeters. FIG. 12C shows diagrammatically the control means and pressure management for the motor of FIG. 12B, whereby changes in pressure within the actuator piston are controlled by applying fluid to and removing fluid from the actuator piston. Confined Space Volume Techniques FIG. 12D shows a schematic of the control means and pressure management of the motor of FIG. 12B, which controls the change in pressure within the actuator piston by varying the volume of the confined space of the actuator piston. Consumption Technology FIG. 13A shows a schematic diagram of a motor having a propulsion system with two or more non-moving expandable actuator pistons in a rotating chamber, the chamber having a centerline with a concentric center of rotation, a two-step piston pumping system in an elongated chamber having different transition cross-sectional areas and circumferences, all assembled to a crankshaft axis and a pressure storage vessel, and an electric starting motor, where the minimum pump and starting motor are powered by solar energy. FIG. 13B shows the motor of FIG. 13A in which the piston pump of the two-step piston pumping system has been replaced by a rotary pump mounted on the main shaft of the motor. Fig. 13C shows a schematic of the motor of Figs. 13A and 13B, which has a propulsion system with a non-moving expandable actuator piston in a rotating chamber, said chamber being concentric with the center of rotation and having four sub-chambers successive to each other, with different transition cross-sectional areas and circumferences, said chamber having a centerline passing through the center of said chamber and rotating around an axle. FIG. 13D shows a schematic of the suspension (including) of the motor of FIGS. 13A and 13B. Drive Belt Figure 13E is a schematic diagram including control means and pressure management for the motor of Figures 13A and 13B. A storage pressure vessel in which the continuously varying internal pressure of the actuator pistons is determined by a separate piston-chamber combination for each of the actuator pistons that is computer controlled. Confined Space Volume Technology FIG. 13F shows pressure management of the expandable pistons of FIG. 13C according to the principle of FIG. 11F, where each actuator piston is managed by two piston-chamber combinations, one for continuously varying pressure and one for adjusting the pressure level to regulate the motor speed/power. FIG. 13G shows a pressurization system for the configuration of FIG. 13F. Confined Space Volume Techniques Figure 14A shows several stages of an actuator piston in which a circular chamber is operating and what is needed to vary the internal pressure of said actuator piston by varying the volume below the pump piston of the connected chamber. FIG. 14B shows the arrangement of FIG. 14A in which a cam wheel connected to the piston rod of the pump piston communicates with a cam of appropriate profile. FIG. 14C shows the arrangement of FIG. 14A in which a cam wheel connected to the piston rod of the pump piston communicates with a cam of appropriate profile. FIG. 14D1 shows a moving circular chamber according to FIG. 13A, in which the pressure of the actuator piston is determined by the pressure of a piston-chamber combination having a cam wheel in communication with the piston of the piston-chamber combination, said cam wheel running on a main axis with a cam having a constant profile. FIG. 14D2 shows a moving circular chamber according to FIG. 13A, in which the pressure of the actuator piston is determined by the pressure of a piston-chamber combination having a cam wheel in communication with the piston of the piston-chamber combination, said cam wheel running on a main axis with a cam having a constant profile. FIG. 14E shows a rim with its suspension in which the configuration of FIG. 14D is incorporated with an auxiliary motor shown as an electric motor rotating the cam profile, and in communication with a channel with an enclosed space of the actuator piston is a pressure regulator according to the configuration of FIG. 16 ("drive by wire"), in communication with a remote speeder. FIG. 14F shows an enlarged detail of a cross section of the piston within the circular chamber of FIG. 14E when the piston is in a first circular position. FIG. 14G shows an enlarged detail of a cross section of the piston within the circular chamber of FIG. 14G when the piston is in a second circular position. FIG. 14H shows the arrangement of FIG. 14E mounted in a gearbox, for example of the planetary gear type, between the rim of the wheel and said circular chamber. BRIEF DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 14I shows a portion of the pressure management system controlling the speed of the motor to which the wheels/propellers are attached, for example. Auxiliary Power Source FIG. 15A shows an H2 fuel cell as the power source for the pressure storage vessel, necessary components, and a recompression pump to pressurize the power lines. FIG 15B shows a combustion motor powered by H2 produced by electrolysis of conductive water. The axle of the combustible drives an alternator which charges a battery, which in turn operates an electric motor in communication with (a) a pump to recompress a pressure reservoir. FIG. 15C shows a combustion motor powered by H2 produced by electrolysis of conductive water, the axle of said combustible material communicating directly from (a) the pump to (a) the crankshaft, which recompresses the pressure storage vessel. FIG. 15D shows a combustion motor powered by H2 produced by electrolysis of conductive water, the axle of said combustible being in direct communication with (a) a rotary pump for recompression of the pressure storage vessel. FIG. 15E shows a capacitor that is electrically charged and in communication with the (a) pump to power an electric motor for recompression of the pressure reservoir. ESVT-CRANKSHAFT DESIGN - MULTIPLE USE OF COMPONENTS Figure 16A shows a scaled up two-way actuator of Figure 16A. 11G-R. FIG. 16B shows a preliminary investigation of the two-way actuator of FIG. 16A. ESVT-CRANKSHAFT DESIGN - MULTIPLE USE OF COMPONENTS Figure 17A shows a schematic diagram of two strokes of the actuator piston according to the diagram. The stroke from the first longitudinal direction to the second longitudinal direction of one cylinder motor is called the power stroke, and the stroke from the first to the second longitudinal direction is called the return stroke. FIG. 17B shows a two cylinder motor ("A" and "B") with strokes according to the diagram. The crankshaft (consisting of two sub-crankshafts) is designed so that the output stroke of each cylinder moves in opposite directions. FIG. 17C shows a two cylinder motor shown in FIG. 11R, where the combustion motor is forced liquid cooled, one of the ESVT pumps is replaced by an inlet/outlet of one sub-crankshaft communicating with the ESVT pump of the other sub-crankshaft, said communication is controlled by a valve actuator shown in FIG. 210E, the operation of said valve actuator is initiated by a cam of a camshaft and driven by said combustion motor, the start of the power stroke of the left cylinder is synchronized with the start of the return stroke of the right cylinder, and the second closed space of one sub-crankshaft is separated from the third closed space of the other sub-crankshaft.

FIG. 17C(l) is an enlarged view of the left side of FIG. 17C and a diagram showing the relationship between the connecting rods of the pistons of both actuators. Figure 17C r. shows an enlarged view of the right side of Figure 17C.
FIG. 17D shows the middle of the power stroke of the left cylinder according to FIG. 17C and the middle of the return stroke of the right cylinder of the motor. FIG. 17D(l) is an enlarged view of the left side of FIG. 17D and a diagram showing the relationship between the connecting rods of both actuator pistons. Figure 17D r. shows an enlarged view of the right side of Figure 17D. FIG. 17E shows the end of the power stroke of the left cylinder and the end of the return stroke of the right cylinder of the motor according to FIG. 17D. FIG. 17E(1) is an enlarged view of the left side of FIG. 17E and a diagram showing the relationship between the connecting rods of the pistons of both actuators. Figure 17E r. shows an enlarged view of the right side of Figure 17E. FIG. 17F shows the beginning of the return stroke of the left cylinder and the beginning of the power stroke of the right cylinder of the motor according to FIG. 17E. FIG. 17F(1) is an enlarged view of the left side of FIG. 17F and a diagram showing the relationship between the connecting rods of the pistons of both actuators. Figure 17F r. shows an enlarged view of the right side of Figure 17F. FIG. 17G shows the middle of the return stroke of the left cylinder and the middle of the power stroke of the right cylinder of the motor according to FIG. 17F. FIG. 17G is an enlarged view of FIG. 17G on the left and the relationship between the connecting rods of both actuator pistons. Figure 17G r. shows an enlarged view of the right side of Figure 17G. FIG. 17H shows the end of the return stroke of the left cylinder and the end of the power stroke of the right cylinder of the motor according to FIG. 17G. FIG. 17H(l) shows the schematic diagram of FIG. 17H on the left and the relationship between the connecting rods of both actuator pistons. Figure 17H r. shows an enlarged view of the right side of Figure 17H. Figure 17C r. shows an enlarged view of the right side of Figure 17C. FIG. 17C(l) is an enlarged view of the left side of FIG. 17C and a diagram showing the relationship between the connecting rods of the pistons of both actuators. Figure 17C r. shows an enlarged view of the right side of Figure 17C. FIG. 17D shows the middle of the power stroke of the left cylinder according to FIG. 17C and the middle of the return stroke of the right cylinder of the motor. FIG. 17D(l) is an enlarged view of the left side of FIG. 17D and a diagram showing the relationship between the connecting rods of both actuator pistons. Figure 17D r. shows an enlarged view of the right side of Figure 17D. FIG. 17E shows the end of the power stroke of the left cylinder and the end of the return stroke of the right cylinder of the motor according to FIG. 17D. FIG. 17E(1) is an enlarged view of the left side of FIG. 17E and a diagram showing the relationship between the connecting rods of the pistons of both actuators. Figure 17E r. shows an enlarged view of the right side of Figure 17E. FIG. 17E(1) is an enlarged view of the left side of FIG. 17E and a diagram showing the relationship between the connecting rods of the pistons of both actuators. FIG. 17E(1) is an enlarged view of the left side of FIG. 17E and a diagram showing the relationship between the connecting rods of the pistons of both actuators. FIG. 17F shows the beginning of the return stroke of the left cylinder and the beginning of the power stroke of the right cylinder of the motor according to FIG. 17E. FIG. 17F(1) is an enlarged view of the left side of FIG. 17F and a diagram showing the relationship between the connecting rods of the pistons of both actuators. Figure 17F r. shows an enlarged view of the right side of Figure 17F. FIG. 17G shows the middle of the return stroke of the left cylinder and the middle of the power stroke of the right cylinder of the motor according to FIG. 17F. FIG. 17G is an enlarged view of FIG. 17G on the left and the relationship between the connecting rods of both actuator pistons. Figure 17G r. shows an enlarged view of the right side of Figure 17G. FIG. 17H shows the end of the return stroke of the left cylinder and the end of the power stroke of the right cylinder of the motor according to FIG. 17G. FIG. 17H(l) shows the schematic diagram of FIG. 17H on the left and the relationship between the connecting rods of both actuator pistons. Figure 17H r. shows an enlarged view of the right side of Figure 17H. FIG. 17I schematically shows two strokes of the actuator piston according to the figure. ESVT-CRANKSHAFT DESIGN - Multiple Use of Components Figure 18A shows two cylinder motors ("A" and "B") with strokes. In FIG. 17A, the crankshaft (consisting of two sub-crankshafts) is designed such that the output stroke of each actuator piston moves in the same (0°) direction. FIG. 18A(1) is an enlarged view of the left side of FIG. 18A and shows the relationship between the connecting rods of both actuator pistons. Figure 18A r. shows an enlarged view of the right side of Figure 18A. Figure 18B shows a simple configuration of two cylinder motors according to Figure 17C, where the combustion motor is forced liquid cooled and has one ESVT pump feeding both actuator pistons, and one The second sealed space of the sub-crankshaft communicates with the third sealed space of the other sub-crankshaft. The start of the power stroke of the left cylinder is synchronized with the start of the power stroke of the right cylinder. FIG. 18B(l) is an enlarged view of FIG. 18B on the left side and shows the relationship between the connecting rods of the pistons of both actuators. Figure 18B r. shows an enlarged view of the right side of Figure 18B. FIG. 18C is a diagram showing the center of the power stroke of the left and right cylinders of the motor according to FIG. 18B. FIG. 18C(l) is an enlarged view of the left side of FIG. 18C and a diagram showing the relationship between the connecting rods of both actuator pistons. Figure 18C r. shows an enlarged view of the right side of Figure 18C. Figure 18D shows the end of the power stroke of the left and right cylinders of the motor according to Figure 18C. FIG. 18D(l) is an enlarged view of the left side of FIG. 18D and a diagram showing the relationship between the connecting rods of the pistons of both actuators. Figure 18D r. shows an enlarged view of the right side of Figure 18D. Figure 18E shows the beginning of the return stroke of the left and right cylinders of the motor according to Figure 18D. FIG. 18E(l) is an enlarged view of the left side of FIG. 18E and a diagram showing the relationship between the connecting rods of the pistons of both actuators. Figure 18E r. shows an enlarged view of the right side of Figure 18E. Figure 18F shows the center of the return stroke of the left and right cylinders of the motor according to Figure 18E. Figure 18F(1) shows an enlarged view of the left figure 18F and an intermediate view thereof. Relationship diagram of the connecting rods of both actuator pistons 18F r. Shows an enlarged view of Figure 18F on the right. FIG. 18G is a diagram showing the return stroke ends of the left and right cylinders of the motor according to FIG. 18F. FIG. 18G1 is an enlarged view of the left side of FIG. 18G and a diagram showing the relationship between the connecting rods of both actuator pistons. Figure 18G r. Shows an enlarged view of the right figure. Figure 18B shows a simple configuration of two cylinder motors according to Figure 17C, where the combustion motor is forced liquid cooled and has one ESVT pump feeding both actuator pistons, and one The second sealed space of the sub-crankshaft communicates with the third sealed space of the other sub-crankshaft. The start of the power stroke of the left cylinder is synchronized with the start of the power stroke of the right cylinder. FIG. 18B(l) is an enlarged view of FIG. 18B on the left side and shows the relationship between the connecting rods of the pistons of both actuators. Figure 18B r. shows an enlarged view of the right side of Figure 18B. FIG. 18B(l) is an enlarged view of FIG. 18B on the left side and shows the relationship between the connecting rods of the pistons of both actuators. Figure 18B r. shows an enlarged view of the right side of Figure 18B. FIG. 18C is a diagram showing the center of the power stroke of the left and right cylinders of the motor according to FIG. 18B. FIG. 18C(l) is an enlarged view of the left side of FIG. 18C and a diagram showing the relationship between the connecting rods of both actuator pistons. Figure 18C r. shows an enlarged view of the right side of Figure 18C. Figure 18D shows the end of the power stroke of the left and right cylinders of the motor according to Figure 18C. FIG. 18D(l) is an enlarged view of the left side of FIG. 18D and a diagram showing the relationship between the connecting rods of the pistons of both actuators. Figure 18D r. shows an enlarged view of the right side of Figure 18D. Figure 18E shows the beginning of the return stroke of the left and right cylinders of the motor according to Figure 18D. FIG. 18E(l) is an enlarged view of the left side of FIG. 18E and a diagram showing the relationship between the connecting rods of the pistons of both actuators. Figure 18E r. shows an enlarged view of the right side of Figure 18E. Figure 18F shows the center of the return stroke of the left and right cylinders of the motor according to Figure 18E. Figure 18F(1) shows an enlarged view of the left figure 18F and an intermediate view thereof. Relationship between connecting rods of both actuator pistons Figure 18F r. Shows an enlarged view of Figure 18F on the right. FIG. 18G is a diagram showing the return stroke ends of the left and right cylinders of the motor according to FIG. 18F. FIG. 18G1 is an enlarged view of the left side of FIG. 18G and a diagram showing the relationship between the connecting rods of both actuator pistons. Figure 18G r. Shows an enlarged view of the right figure. CRANKSHAFT DESIGN (CRANKSHAFT DESIGN) - Multiple Use of Components Figure 19A shows one cylinder motor based on Figures 11B, 11C, where several parts are further considered. That is, the auxiliary power source is a combustion motor that burns H2, derived from the electrolysis of H20. Figure 19B shows a two cylinder motor based on Figure 19A. Based on Figure 19 A, the two cylinders are mirror arranged in the center line of the connection, the third enclosed space (outlet) communicates with each other through the connection of the two sub-crankshafts, and the second The closed space (inlet) communicates with the outside of the crankshaft (with a check valve), and the crankshaft (consisting of two sub-crankshafts) has the power stroke of each actuator piston the same ( It is designed to move simultaneously in the 0°) direction (synchronized). Figure 19B(l) shows an enlarged view of the left side of Figure 19B. Figure 19B r. shows an enlarged view of the right side of Figure 19B. Figure 19C shows a two-cylinder motor based on Figure 19A, where the corresponding enclosed spaces (here, the third enclosed space) are connected to each other via a sub-crankshaft, and the second enclosed space are connected together externally (with a check valve) and the crankshaft (consisting of two sub-crankshafts) is connected together (with a check valve) so that each actuator piston has the same power stroke ( 180°) direction (asynchronously). Figure 19C l. shows an enlarged view of the left side of Figure 19C. Figure 19C r. shows an enlarged view of the right side of Figure 19C. 19620 BRIEF DESCRIPTION OF THE DRAWINGS In the following, preferred embodiments of the invention will be described with reference to the drawings. Figure 21A shows a conical longitudinal section. The chamber of constant, the common (pressure) boundary of the pump, and the maximum working force characteristic showing the convex and conical shape of the sides, the longitudinal section between said boundaries. Figure 21B shows the chamber of Figure 21A (10 bar overpressure) and (in dashed lines) an alternative chamber geometry (16 bar overpressure). Identical chamber, length. FIG. 22 shows a conical longitudinal section of the chamber of FIG. 21. Figure 3 shows an expansion chamber as a continuation of said chambers. Figure 23 shows an advanced conical chamber with constant maximum working force characteristics of the pump, from the inner conical part of the chamber to the inside of a straight line at a second longitudinal position parallel to the central axis of the chamber shows a certain internal concave transition. FIG. 24 shows the expandable deformable piston not moving itself from the second longitudinal position to the first longitudinal position because the inner wall of the chamber of FIG. 23 is parallel to the central axis. FIG. 25 is a diagram showing a constant thrust chamber connected to a hose with a hose nipple as an outlet. 19630 BRIEF DESCRIPTION OF THE DRAWINGS Figure 30A shows the circular chamber of Figure 12B with the piston moving within the stationary chamber. FIG. 30B shows the circular chamber of FIGS. 13C and 14D without the piston moving. Here we have a circular chamber and subchamber design identical to the design of Figure 30A. FIG. 31A shows FIG. 14D, with portion XX shown. FIG. 31B shows a scaled-up detail of section XX of the chamber of FIG. 31A. Mathematical Description of Circular CHAMBER and Piston Figure 32(A) shows that the walls of the chamber and a plane orthogonal to the base circle intersect in a circle whose center is on the base circle. Figure 32B is a cross-section of the piston boundary. Figure 32(C) shows the required cap area and internal volume cap geometry. For the area and internal volume of the cap where only the values of a and h are required, see equations (2.1) and (2.2). The radius of the virtual sphere is given by (2.3). Figure 32D shows a piston with an end cap. Figure 32E shows a piston with an end cap within a transparent Fermi tube chamber. Figure 32F shows the pure contact area between the piston and the chamber, visible inside the transparent chamber wall. Figure 32G shows the contact area between the piston and the chamber. Figure 32H shows a cross section of the chamber wall. Chamber reaction forces are marked in gray. The total force on the cross section is perpendicular to the chamber wall. The cross section is the (variable) length of the cross section shown and the force value proportional to the internal pressure of the piston. Figure 32I shows the section of Figure 32H with an additional section to provide an open view. FIG. 32(J) is the same as FIG. 32(H), and the red vector is the vertical gray force component. Figure 32K shows Figure 32J with an additional section to provide an open view. Figure 32(L) shows Figure 32(J). In Figure 32(J), the actual sliding force along the wall surface is shown in blue. This figure is a projection of the red vector at right angles to the chamber wall. Figure 32M shows Figure 32L with an additional section to provide an open view. 19640 BRIEF DESCRIPTION OF THE DRAWINGS Figure 40A shows a longitudinal pump with a piston, comprising support means, an O-ring, a flexible impermeable layer, and finally supported by a foam in a first longitudinal position. A cross-sectional view is shown. Figure 40B shows details of the suspension of the support means, O-ring and flexible impermeable layer vulcanized together. FIG. 40C shows a longitudinal cross-section of the piston of FIG. 40A in a second longitudinal position. FIG. 41A shows a top view of the piston of FIG. 40A and a cross-sectional view of the chamber from a first longitudinal position. FIG. 41B shows details of the suspension on the O-ring and lying spring support means of the piston of FIG. 40A. FIG. 41C shows a cross-section of the chamber with the piston of FIG. 40A in a second longitudinal position. FIG. 41D shows a bottom view of the piston of FIG. 40A and a cross-sectional view of the chamber in a first longitudinal position, showing helical 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 a first longitudinal position, showing helical reinforcement of the impermeable sheet. FIG. 42A shows a longitudinal section of a piston comprising a support means, an O-ring and a flexible impermeable layer, finally in a first longitudinal position at an angle relative to the central axis of the chamber; It was described in Figure 42B shows details of the suspension of support means, O-ring and flexible impermeable layer vulcanized together. Figure 42C shows a longitudinal section of the piston of Figure 42A in a second longitudinal position. 19650 BRIEF DESCRIPTION OF THE DRAWINGS Figure 50 shows a top view of the foam piston, specifically the suspension of the reinforcing pin. FIG. 51 is a diagram showing a longitudinal section AA of a PU foam piston. FIG. 52 shows a longitudinal section BB of the piston of FIG. 50. 19650-1 DESCRIPTION OF THE DRAWINGS Figure 55 A shows the piston in the first longitudinal position of the advanced pump, said piston being rotatably fixed by magnetic forces to the holder plate of the holder attached to the piston rod. It has a metal pin. Figure 55B shows an enlarged longitudinal section PP of the holder plate attached to the holder. Figure 55C shows an enlarged view of the holder plate on the holder from Figure 55B. FIG. 55D shows enlargement of protrusions in the recess between the holder and the holder plate for improved squeezing of the impermeable layer. Figure 55E shows an alternative solution for reinforcing and securing the foam to that shown in Figures 55A-D. Figure 55F shows an enlargement of the holder plate on the holder from Figure 55E. FIG. 55G shows a solution for automatic clockwise rotation of the foam reinforcement pin as the piston runs towards the first longitudinal position. Figure 55H shows an enlargement of the holder plate on the holder from Figure 55G. 19660 BRIEF DESCRIPTION OF THE DRAWINGS FIG. 60 is a longitudinal cross-sectional view and a cross-sectional view of both ends of a container piston. FIG. 61 shows details of both ends of the container piston of FIG. 60. Figure 62 shows a container-type piston at the beginning and end of a stroke in a chamber (see 19620-) where the force on the piston rod is constant. Figure 62 shows a container-type piston at the beginning and end of a stroke in a chamber (see 19620-) where the force on the piston rod is constant. Figure 63 shows the force from the actuator piston to the longitudinal chamber wall. Figure 64A shows an elliptical piston in a chamber with a central longitudinal axis at a 20° angle. FIG. 64B shows an ellipsoidal piston in a chamber with a central longitudinal axis at a 10° angle. 19680-2 BRIEF DESCRIPTION OF THE DRAWINGS Figure 80A shows a chamber of a pump according to section 19620, with a piston according to section 19680 in three different longitudinal positions, said piston wall comprising a separate rotatable portion, and said piston according to section 19680 in three different longitudinal positions; It conforms to the slope of the chamber wall and its surface is hermetically connected to said chamber wall and to said piston wall. FIG. 80B shows a scaled-up detail of the contact area when the piston is in a first longitudinal position. FIG. 80C shows a scaled-up detail of the contact area when the piston is in a second longitudinal position. Figure 80D shows the separate portions when the piston is in the second longitudinal position. FIG. 80E shows an alternative spherical shape of a separate portion of that shown in FIGS. 80A-C. FIG. 80F shows an alternative half-rond shape of a separate portion of that shown in the figure. 80A-C are vulcanized on a (scaled up) piston in accordance with Section 19660 and apply when said piston is in a second longitudinal position. FIG. 80G shows a piston according to FIG. 80F, with a separation located below a line passing through the longitudinal midpoint of the flexible wall of said piston. Figure 80H shows a piston according to Figure 80C, with the separation located below a line passing through the longitudinal midpoint of the flexible wall of the piston. 801 shows the piston of FIG. 80J in a second longitudinal position of the chamber according to section 19620. FIG. 80J shows an enlarged view of the piston of FIG. 801 as generated. FIG. 81A shows a chamber of a pump according to section 19620 having an inflatable piston according to section 19680 on three different sides. The piston wall comprises two separate rotatable parts adapted to the slope of the chamber wall, the surfaces of which are sealingly connected to the chamber wall and to the piston wall in a longitudinal position. . FIG. 81B shows a scaled-up detail of the contact area when the piston is in a first longitudinal position. FIG. 81C shows an enlarged detail of the contact area when the piston is positioned between a first longitudinal position and a second longitudinal position. FIG. 81D shows the piston placed in a second longitudinal position (scaled up). FIG. 82A shows a chamber of a pump according to section 19620, with an expandable piston according to section 19680 in three different longitudinal positions, said piston wall comprising two parts with different circumferences, where: The maximum comprises the contact area between the chamber wall and the piston wall. Figure 82B shows a scaled-up detail of the contact area when the piston is in a first longitudinal position. FIG. 82C shows an enlarged detail of the contact area when the piston is positioned between a first longitudinal position and a second longitudinal position. Figure 82D shows the piston placed in a second longitudinal position (scaled up). FIG. 83A shows the piston of FIG. 82D including a non-flat piston rod. FIG. 83B shows the piston of FIG. 83A in an expanded first longitudinal position. Figure 83C shows the piston of Figure 83B with a clamp on the piston rod that holds the piston in place when retracted. Figure 83D shows the piston of Figure 83C with the foam inserted through the closed space of the piston rod. FIG. 83E shows the piston of FIG. 83D after insertion and curing of the unclamped foam. Figure 83F shows the piston of Figure 83E in a second vertical position with a pressure sensor and an expansion valve. Figure 83G shows an enlargement of the pressure sensor and expansion valve of the piston of Figure 83E. FIG. 83H shows the piston of FIG. 83E in a second vertical position with a different type of pressure sensor and expansion valve than shown in FIG. 83F or 83G. Figure 83I shows an enlargement of the pressure sensor and expansion valve of the piston of Figure 83H. Figure 83J shows the piston of Figure 83E in a second vertical position with a different type of pressure sensor and expansion valve than shown in Figures 83F, 83G or 83H. Figure 83K shows an enlargement of the pressure sensor and expansion valve of the piston of Figure 83J. FIG. 84A shows, for example, the piston of FIG. 83H for compact applications, where the tension spring provides an expansion force on the piston wall in addition to the force derived from the expandable toroid in communication with the enclosed space; Thereby, the pressure side of the pump piston has foam inside to keep that part properly inflated under external pressure. Figure 84B has foam inside the entire piston, communicating through the exhaust hole to the unpressurized exterior of the piston, assembled inside the piston wall, and communicating with the enclosed space of the piston; Figure 84A; shows an improved piston based on Figure 84C shows the piston of Figure 84A, where the low pressure side of the piston wall is a flat cone. FIG. 84D shows a spherical piston on the second and first longitudinal positions of the chamber with separate parts on the outer wall as shown. 80F, 80G, 80J for oval pistons. Figure 84E shows a spherical piston with a piston wall, said piston wall comprising two parts with different circumferences, where the largest are the chamber wall and the piston wall (for the oval piston type, 82A-D), the pistons are shown in second and first vertical positions. Figure 84F shows a spherical piston with an expandable toroid as a separate part, as shown in Figure 84B for an elliptical piston. 19690-2- BRIEF DESCRIPTION OF THE PTREFERRED EMBODIMENT FIG. 90A shows a rotating piston in a circular chamber, the piston being connected to an axle by a connecting rod, said axle and the connecting rod comprising channels communicating with each other. FIG. 90B shows an enlarged view of the connecting rod and axle, and details of the tooth assembly between the axle and the connecting rod. FIG. 90C shows an enlargement of the connecting rod to which the piston is attached, based on FIG. 14F, when the piston is positioned in the first circular position. FIG. 90D shows an enlargement of the connecting rod to which the piston is attached, based on FIG. 14G, when the piston is positioned in the second circular position, together with the CT and/or ESVT system. 90E shows the structure of FIG. 90A in which the channel in the axle communicates with the CT pressure management system according to FIG. 11A, and FIG. 11D shows the structure of FIG. 11A for the connection rod and axle junction. show. FIG. 90F shows the configuration of FIG. 90A in which the channel in the axle communicates with the ESVT-pressure management system according to FIG. 11(G), and the configuration of FIG. 11T of the axle and communication rod joint. FIG. 90G shows the structure of FIG. 90A where the channel in the axle communicates with the ESVT-pressure management system described in FIGS. 11I and 11T to connect the connecting rod to the axle. Figure 90H shows a preferred embodiment based on the configuration of Figure 90G in a camshaft combination that controls the timing of the ESVT system, while energy is derived from the electrolysis of H2O from a combustion motor driven by H2O. can get. Multiple moving pistons are shown in the chamber (in the same circular position). Figure 901 shows four moving pistons in a chamber, the space within each piston communicating with an enclosed space within each connecting rod, the enclosed space communicating with the enclosed space of the axle, and the space within each piston communicating with the enclosed space within each connecting rod. The piston is moving around. FIG. 90J shows an enlarged view of the joint between the connecting rod and the axle of FIG. 901 with the ESVT system. FIG. 90K shows the ESYT pressure management system according to FIG. 11I and the configuration of FIG. 901 in which the joint and channel in the axle are in communication according to FIGS. 11T and 90J. FIG. 90l shows a preferred embodiment of a motor based on the configuration of FIG. 90K in a camshaft combination that controls the timing of the ESVT-system. On the other hand, energy is obtained from a combustion motor driven by H2, derived from the electrolysis of H2O. A single moving chamber around the piston is shown. FIG. 91A shows a rotating circular chamber in which a piston is arranged, the piston being connected to an axle by a connecting rod, said axle and the connecting rod comprising a channel. FIG. 91B shows an enlarged view of the assembly details of the connecting rod and connecting rod axle of FIG. 91A, the bearing between the axle and the connecting rod, and the channel communicating the intermediate bodies with each other. This configuration may preferably be combined with a CT system. Similar combinations are possible with CT and/or ESVT systems, as shown in FIGS. 90K-90L (inclusive). FIG. 91(C) is a cross-sectional view of a hub with a connecting rod and an axle groove, a bore bearing, and teeth and grooves for fixing the position of a stationary piston. FIG. 91D shows the cross-section shown in FIG. 91C, where rotation of the bearing is provided by rotation of the hub of the spokes of the chamber. FIG. 91E is a cross-sectional view of a hub with connecting rod grooves and axle grooves, where the reduced axle diameter provides constant communication between the grooves (from 19619-EP). Figure 3 shows multiple rotating pistons in parallel chambers. FIG. 92A shows a three-cylinder motor with a piston rotating about a main central axis, the chambers being interconnected, and a gearbox mounted on the assembly, the main axis communicating with the main central axis of the piston. are doing. This structure can preferably be combined with an ESVT system. Figure 92B shows the three cylinder motor on the main axle of Figure 92A, with each side of the motor being an assembled variable pitch wheel communicating with a corresponding pitch wheel on the vehicle axle. Low pitch mode (Variomatic(R)): low speed - this structure can be preferably combined with an ESVT system. Figure 92C is the same as Figure 92B, but at higher speeds where the pitch of the wheels is reversed. Figure 3 shows a plurality of moving chambers transmitting torque to a central axis. Figure 93A shows a three cylinder motor in which the chamber rotates, torque is transmitted to a main central shaft, and an external gearbox communicates with said shaft. This structure can preferably be combined with an ESVT system. Figure 93B shows an enlarged view (4:1) of the left corner of the construction of the central axis of the motor. The present invention will be explained in detail below using the drawings. A cross section refers to a cross section perpendicular to the direction of movement of the piston and/or the chamber, and a longitudinal section refers to a cross section in the direction of movement. FIG. 100 shows a so-called indicator diagram of a one-stage single-acting piston pump with a cylinder and a piston of fixed diameter. FIG. 102A is an indicator diagram of a piston pump according to part A of the invention, showing the piston moving option, and part B showing the chamber moving option. FIG. 102B shows an indicator diagram of a pump according to the invention in which, from a certain point in the pump stroke, the cross section increases again by increasing the pressure. FIG. 103A shows a longitudinal section of the pump with fixed and different areas of the cross section of the pressurized chamber and the piston, which changes dimensions radially and axially during the stroke. This piston arrangement is shown at the beginning and end of the pump stroke (first embodiment). FIG. 103B shows an enlargement of the piston configuration of FIG. 103A at the beginning of the stroke. FIG. 103C shows an enlargement of the piston configuration of FIG. 103A at the end of the stroke. FIG. 103D shows a longitudinal section of the chamber of the floor pump according to the invention, the operating force is almost constant, and for comparison, the cylinders of the existing low pressure (dotted line) and high pressure (dotted line) pumps are shown simultaneously. Figure 104A shows a longitudinal cross-section of the pump with fixed and different areas of the cross-section of the pressurized chamber and a piston that changes dimensions radially/partially axially during the stroke, with the piston arrangement are shown at the beginning and end of the pump stroke (second embodiment). Figure 104B shows an enlargement of the piston configuration of Figure 104A at the beginning of the stroke. FIG. 104C shows an enlargement of the piston configuration of FIG. 104A at the end of the stroke. Figure 104D shows sections A-A of Figure 104B. FIG. 104E shows cross section BB of FIG. 104C. Figure 104F shows an alternative solution to the load portion of Figure 104D. FIG. 105A shows a longitudinal section of the pump with fixed and different regions of the cross section of the pressurizing chamber and a piston that changes dimensions radially and axially during the stroke. This piston arrangement is shown at the beginning and end of the pump stroke (third embodiment). Figure 105B shows an enlargement of the piston configuration of Figure 105A at the beginning of the stroke. FIG. 105C shows an enlargement of the piston configuration of FIG. 105A at the end of the stroke. Figure 105D shows section CC of Figure 105A. Figure 105E shows sections D-D of Figure 105A. Figure 105F shows the pressurized chamber of Figure 105A with piston means having sealing means made of a composite of materials. Figure 105G shows an enlargement of the piston means of Figure 105F during a stroke. Figure 105H shows the expansion of the piston means of Figure 105F at the end of the stroke, both while still being pressurized and while no longer pressurized. FIG. 106A shows a fourth embodiment of a longitudinal section of the pump with fixed and different regions of the cross section of the pressurized chamber and a piston that changes dimensions radially and axially during the stroke. This piston placement is shown at the beginning and end of the pump stroke. Figure 106B shows an enlargement of the piston arrangement of Figure 106A at the beginning of the stroke. Figure 106C shows an enlargement of the piston arrangement of Figure 106A at the end of the stroke. FIG. 106D shows a fifth embodiment of the pressurized chamber of FIG. 106A and a piston that changes dimensions radially and axially during the stroke, with the piston positioning changing at the beginning and end of the pump stroke. shown. Figure 106E shows an enlargement of the piston configuration of Figure 106D at the beginning of the stroke. Figure 106F shows an enlargement of the piston configuration of Figure 106D at the end of the stroke. FIG. 107A shows a longitudinal section of a pump with a recess in the wall of the pressurized chamber with fixed dimensions and a sixth embodiment of a piston that changes dimensions radially and axially during the stroke . In this case, the placement of the piston is indicated at the beginning and end of the pump stroke. FIG. 107B shows an enlargement of the piston configuration of FIG. 105A at the beginning of the stroke. Figure 107C shows an enlargement of the piston configuration of Figure 105A at the end of the stroke. Figure 107D shows section EE of Figure 107B. Figure 107E shows section FF of Figure 107C. FIG. 107F shows an example of a cross-section created by Fourier series expansion of a pressurized chamber with decreasing cross-sectional area but constant circumferential size. Figure 107G shows a variation of the pressurized chamber of Figure 107A. The deformation of the pressurized chamber in Figure 107 A has a longitudinal cross-section with a fixed cross-section designed to decrease in area while remaining approximately constant or decreasing to a lesser extent during the pump stroke. have Figure 107H shows cross sections GG (dotted line) and HH of the longitudinal section of Figure 107G. Figure 107I shows cross sections GG (dotted line) and II of the longitudinal section of Figure 107H. Figure 107J shows a variation of the piston of Figure 107B in section HH of Figure 107H. FIG. 107K shows another example of a cross-section created by Fourier series expansion of a pressurized chamber where the cross-sectional area decreases while the circumferential size remains constant. FIG. 107L shows an example of an optimized convex shape of the cross section under certain constraints. FIG. 107M shows an example of an optimized non-convex shape of a cross section under certain constraints. FIG. 108A shows a longitudinal cross-section of a pump with a convexity on the wall of the pressurized chamber with fixed dimensions and a seventh embodiment of a piston that changes dimensions radially and axially during the stroke. This piston arrangement is shown at the beginning and end of the pump stroke. Figure 108B shows an enlargement of the piston configuration of Figure 105A at the beginning of the stroke. FIG. 108C shows an enlargement of the piston configuration of FIG. 105A at the end of the stroke. FIG. 109A shows a longitudinal cross-section of the pump with fixed and different regions of the cross-section of the pressurized chamber and eight embodiments of the piston with varying radial and axial dimensions during the stroke. This piston placement is shown at the beginning and end of the pump stroke. Figure 109B shows an enlargement of the piston configuration of Figure 109A at the beginning of the stroke. Figure 109C shows an enlargement 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. FIG. 110A shows a ninth embodiment of a piston similar to the one in FIG. 109A, with fixed different regions of the cross section of the pressurized chamber. FIG. 110B shows an enlargement of the piston of FIG. 110A at the beginning of the stroke. FIG. 110(C) shows an enlarged view of the piston of FIG. 110(A) at the end of the stroke. FIG. 111A shows a tenth embodiment of a longitudinal section of the pump with fixed different regions of the cross section of the pressurized chamber and a piston that changes dimensions radially and axially during the stroke. This piston placement is shown at the beginning and end of the pump stroke. FIG. 111B shows an enlargement of the piston of FIG. 111A at the beginning of the stroke. FIG. 111C shows an enlargement of the piston of FIG. 111A at the end of its stroke; FIG. 112A shows a longitudinal section of the pump with fixed different regions of the cross section of the pressurized chamber and an eleventh embodiment of the radially and axially varying piston. Dimensions during stroke - Piston placement is shown at the beginning and end of the pump stroke. Figure 112B shows an enlargement of the piston of Figure 112A at the beginning of the stroke. Figure 112C shows an enlargement of the piston of Figure 112A at the end of its stroke. FIG. 113A shows a longitudinal section of the pump with variable different areas of the cross section of the pressurized chamber and a piston with fixed geometric dimensions. This combined arrangement is shown at the beginning and end of the pump stroke. FIG. 113B shows an expanded array of combinations at the beginning of a pump stroke. FIG. 113C shows an expanded array of combinations during a pump stroke. FIG. 113D shows an enlargement of the combination array at the end of the pump stroke. FIG. 114 shows a longitudinal section of the pump with variable different areas of the cross section of the pressurized chamber and a piston with variable geometric dimensions. The combination placement is shown at the beginning, middle and end of the pump stroke. 653 BRIEF DESCRIPTION OF THE DRAWINGS Figure 201 A shows a longitudinal section of a non-moving piston in a non-pressurized cylinder in a first longitudinal position, the piston being shown in its production size and when pressurized. . Figure 201B shows the contact pressure of the pressure piston of Figure 201A on the wall of the cylinder. FIG. 202A shows a longitudinal cross-section of the piston of FIG. 201A in the first (right) and second (left) longitudinal positions of the cylinder, with the piston being unpressurized. Figure 202B shows the contact pressure of the piston of Figure 202A on the wall of the cylinder in a second vertical position. Figure 202C shows a longitudinal section of the piston of Figure 201A in the cylinder at a second longitudinal position, the piston being pressurized at the same pressure level as the one in Figure 201A, and also in the first longitudinal position. The piston in (production) size is also shown. Figure 202D shows the contact pressure on the cylinder wall at the second longitudinal position of the piston of Figure 202C. FIG. 203A shows a longitudinal section of the piston of FIG. 201A within the cylinder in a first longitudinal position indicated by its production size and pressurized while the piston is under pressure in the chamber. Figure 203B shows the contact pressure of the piston of Figure 203A on the wall of the cylinder. FIG. 204A is a longitudinal cross-sectional view of a non-pressurized cylinder at a second longitudinal position of a non-moving piston according to the present invention, shown in production size and pressurized to a constant level. Figure 204B shows the contact pressure of the pressure piston of Figure 204A on the wall of the cylinder. Figure 204C shows a longitudinal cross-section of a non-moving piston according to the present invention in a second longitudinal position indicated by production size and in a first longitudinal position when pressurized to the same level as in Figure 204A. Shown below. Figure 204D shows the contact pressure of the piston of Figure 204C on the wall of the cylinder. FIG. 205A shows the longitudinal cross-section of the piston of FIG. 204A in a second longitudinal position, its production size, and when pressurized, in an unpressurized cylinder. Figure 205B shows the contact pressure of the pressure piston of Figure 205A on the wall of the cylinder. FIG. 205C shows a longitudinal cross-section of the piston of FIG. 204A in the cylinder in a second longitudinal position, the piston having its production size and, when pressurized, receiving pressure from the cylinder. Figure 205D shows the contact pressure of the piston of Figure 205C on the wall of the cylinder. FIG. 206A shows a first embodiment of a piston that includes a longitudinal section of the chamber with fixed different regions of cross-section and a textile reinforcement that changes dimensions radially and axially during the stroke. The piston arrangement is shown first, pressurized at the end of the stroke, and depressurized for its production size. Figure 206B shows an enlargement of the piston of Figure 206A at the beginning of the stroke. Figure 206C shows an enlargement of the piston of Figure 206A at the end of its stroke. FIG. 206D shows a three-dimensional view of a reinforcing matrix of elastic fibrous material placed on the wall of the container when the container is inflated. Figure 206E shows the pattern of Figure 206D when the walls of the container are expanded. Figure 206F shows a three-dimensional view of the reinforcing pattern of inelastic fibrous material placed on the wall of the container when inflating the piston. Figure 206G shows the pattern of Figure 206F when the container wall is expanded. Figure 206H shows manufacturing details of a piston with fiber reinforcement. Figure 207A shows a longitudinal section of the chamber with fixed different areas of cross-section and a piston with fiber reinforcement (trellis effect) with radially and axially varying dimensions of the elastic material of the wall during the stroke. Showing a second embodiment, the piston arrangement is first shown and pressurized at the end of the stroke, where it is pressurized without pressurizing the 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 its stroke. Figure 208A shows a longitudinal cross-section of a chamber in which different areas of the cross-section are fixed, and the third embodiment of the piston changes the radial and axial dimensions of the elastic material of the wall during the stroke. The arrangement of the piston is shown in a first longitudinal position, pressurized and unpressurized manufacturing size in a second longitudinal position. Figure 208B shows an enlargement of the piston of Figure 208A at the beginning of the stroke. Figure 208C shows an enlargement of the piston of Figure 208A at the end of its stroke. FIG. 208D shows a plan view of the piston of FIG. 208A with a reinforced wall in a plane through the central axis of the piston, left: a first longitudinal position, right: a second longitudinal position . Figure 208E shows a top view of a piston with rebar in the wall in a plane that partially passes through the piston's central axis and partially passes outwardly through the piston's central axis, similar to the piston in Figure 208A, on the left side. is the first longitudinal position and the right side is the second longitudinal position. Figure 208F shows a top view of a piston similar to the one in Figure 208A, with reinforcing bars in the walls in a plane that does not pass through the central axis of the piston - left: first longitudinal position, right: second longitudinal position . Figure 208G shows manufacturing details of a fiber reinforced piston. FIG. 209A shows a fourth embodiment of a piston with a longitudinal cross-section of the chamber with fixed different regions of cross-section with different circular lengths and an "octopus" device, which is expandable. The tentacle (piston arrangement is shown in the first longitudinal position of the chamber and pressurized in the second longitudinal position of the chamber, limiting the extension of the vessel wall by the tentacle) Figure 3 shows a longitudinal section of the chamber, including the chamber (not pressurized). Figure 209B shows an enlargement of the piston of Figure 209A in a first longitudinal position of the chamber. Figure 209C shows an enlargement of the piston of Figure 209A in a second longitudinal position of the chamber. Figure 210A shows how the pressure within the piston changes due to expansion, e.g. via a Schrader valve, placed in a check valve in the handle and/or piston rod, and the enclosed space balances the change in volume of the piston during the stroke. 206 shows the embodiment of FIG. Figure 210B shows a bushing instead of an expansion valve that allows connection to an external pressure source. Figure 210(C) shows details of the check valve rod guide. FIG. 210D shows the flexible piston of the check valve within the piston rod. FIG. 210E shows that of FIG. 206 in which the volume of the enclosed space of FIGS. 210A-D has been replaced by a pressure source and an inlet valve for expanding the piston from the pressure source and an outlet valve for pressure release to the pressure source. FIG. 21 ID is an enlarged detail view of the valve-valve actuator combination according to FIG. 211D; FIG. 210F shows the embodiment of FIG. 10E, where there is a steerable valve and a jet or nozzle shown as a black box. Figure 211A shows that during the stroke the pressure within the piston may be kept constant, a second closed space may be expanded via a Schrader valve located within the handle, and a second closed space may be expanded via the piston device. 1, the piston may be inflated by a Schrader valve+valve actuator device, and the outlet valve of the chamber may be manually controlled by a rotatable pedal. . FIG. 211B shows a piston arrangement and a bearing in which the piston arrangement communicates between a second enclosed space and a first enclosed space. FIG. 211C shows an alternative piston arrangement that accommodates varying longitudinal cross-sectional areas within the piston rod. FIG. 211D shows an enlargement of the expanded configuration of the piston of FIG. 211A at the end of the stroke. FIG. 211E shows an enlargement of the bypass arrangement of the valve actuator for closing and opening the outlet valve. FIG. 211E' shows an enlargement of the bypass arrangement of the valve actuator for closing and opening the outlet valve. Figure 211F shows an enlargement of the automatic closing and opening arrangement of the outlet valve, showing a similar system for obtaining a predetermined pressure value (dashed line) in the piston. FIG. 211G shows an enlargement of the expansion configuration of the piston of FIG. 211A, the piston including a combination of a valve actuator and a spring force actuated cap to automatically expand the piston from the chamber to a predetermined pressure. It is characterized by making it possible. FIG. 211H shows an alternative solution to the one in FIG. 211G that includes a combination of a valve actuator and a spring positioned below the piston of the valve actuator. Figure 212 shows an arrangement in which the pressure within the container may depend on the pressure within the chamber. FIG. 213A shows a longitudinal section of a chamber with an elastic or flexible wall with different regions of cross-section and a piston with a fixed geometric size. This combined arrangement is shown at the beginning and end of the pump stroke. Figure 213B shows an expanded array of combinations at the beginning of the pump stroke. Figure 213C shows an expanded array of combinations during a pump stroke. FIG. 213D shows an enlargement of the combination array at the end of the pump stroke. FIG. 214 shows a longitudinal section of a chamber with an elastic or flexible wall with different regions of cross-section and a piston with different geometrical dimensions. This combined arrangement is shown at the beginning, middle, and end of the stroke. Figure 215A shows an example of a cross-section created by Fourier series expansion of a pressurized chamber where the cross-sectional area decreases while the perimeter size remains constant. FIG. 215B shows a deformation of the pressurized chamber of FIG. 207A, which is a fixed It has a longitudinal section with a transverse section. Figure 215C shows cross sections GG (dotted line) and HH of the longitudinal section of Figure 215B. Figure 215D shows cross sections GG (dotted line) and II of the longitudinal section of Figure 215C. FIG. 215E shows another example of a cross-section created by Fourier series expansion of a pressurized chamber where the cross-sectional area decreases while the perimeter size remains constant. FIG. 215F shows an example of an optimized convex shape of the cross section under certain constraints. Figure 216 shows a combination in which the piston moves within the cylinder beyond the 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 mobile power unit suspended below a parachute. Figure 218B shows details of the mobile power supply unit. 507 Description of the Drawings Figure 301 shows a first embodiment of a valve actuator in a clip-on valve connector to which a Schrader valve can be coupled. Figure 301A shows an enlargement of the detail of Figure 301 with channels around the piston, and Figure 301B shows section GG of Figure 301A. Figure 302 shows a second embodiment of a valve actuator in a universal clip-on valve connector with a streamlined actuation pin. Figure 302A shows an enlargement of the detail of Figure 302, and Figure 302B shows section HH of Figure 302A. FIG. 303 shows a third embodiment of a valve actuator in a squeeze-on valve connector. Figure 303A shows an enlargement of the detail of Figure 303. Figure 304 shows a valve actuator including an actuation pin and a cylinder wall in a permanent assembly (eg, from a chemical plant). Figure 305 shows a fourth embodiment of a valve actuator within a universal valve connector. 19597 BRIEF DESCRIPTION OF THE DRAWINGS Preferred embodiments of the invention will now be described with reference to the drawings. The present invention will be described in detail below with reference to the drawings and drawings. A cross section refers to a cross section perpendicular to the direction of movement of the piston and/or the chamber, and a longitudinal section refers to a cross section in the direction of movement.

Fig. 401A shows a top view of the floor pump type pump of Fig. 401B, this combination allows lines XX, YY or ZZ to rotate relative to the floor surface, but the angle is not limited by the suspension. Fig. 401B shows a rear view of the floor pump of Fig. 401A.
Fig. 402A shows a top view of a floor pump type pump of Fig. 402B, where the combination is movable in three dimensions relative to the surface, but the angle is limited by the spring force of the transition between the combination and the base. Fig. 402B shows a rear view of the floor pump. FIG. 402C shows a top view of the pump of FIG. 402B with the handle moved to a position in front of its rest position. FIG. 402D shows a top view of the pump of FIG. 402B with the handle moved to a position behind its rest position. FIG. 402E shows a top view of the pump of FIG. 402B with the handle moved to a left position in front of its rest position. FIG. 402F shows a top view of the pump of FIG. 402B with the handle moved to a left position behind its rest position. FIG. 402G shows a top view of the pump of FIG. 2B with the handle moved to a right position before its position when disabled. FIG. 402H shows a top view of the pump of FIG. 402B with the handle moved to a right position behind its rest position. Fig. 403A shows a side view of a floor pump with a flexible transition between the combination and base chambers. Fig. 403B shows a close-up of the transition of Fig. 403A. Fig. 403C shows a rear view of a floor pump with another flexible transition between the combination chamber and base, and Fig. 403D shows a close-up of the transition of Fig. 403C. FIG. 404A shows a rear view of a floor pump with a carburetor that allows the piston rod to move laterally in combination. FIG. 404B shows an enlargement of the cross section of the cab. FIG. 404A shows no lateral movement when the piston rod is fully extended. FIG. 404C shows the cross section of FIG. 404B when the piston rod is fully extended and rotated to the left. FIG. 404D shows an enlargement of the cross section of the cab. FIG. 404A shows the case where there is no lateral movement when the piston rod is not extended. FIG. 404E shows the cross section of FIG. 404D when the piston rod is not extended with lateral movement of the piston rod to the left. Fig. 405A shows a top view of the floor pump type of Fig. 405B, where the angle between the centerline of the assembly and the centerline of the opposite handle portion is less than 180°. Fig. 405B shows a side view of the handle of the floor pump of Fig. 405A. Fig. 406A shows a top view of the floor pump type of Fig. 406B where the angle between the centerline of the chamber and the centerline of the opposing handle portion is greater than 180°. Fig. 406B shows a side view of the handle of the floor pump of Fig. 406A.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
Figures 1-3 address the limitations of the piston wall extension, including limitations to longitudinal extension when the piston is subjected to pressure in the chamber, and limitations allowing lateral expansion when moving from the second longitudinal position to the first longitudinal position.

The longitudinal extension of the wall of the container piston can be limited in several ways. This may be done by reinforcing the walls of the container, for example by using textile and/or fiber reinforcement. It can also be carried out inside the chamber of the container where the expansion body is placed with limited expansion while connected to the wall of the container. Other methods may be used, such as pressure management in a chamber between two walls of the container, pressure management in the space above the container, etc.

The expansion behavior of the container wall may depend on the type of expansion restriction used. Furthermore, the retention of the piston moving on the piston rod while expanding may be guided by mechanical stops. The position of such stops may depend on the piston-chamber combination used. This also applies when guiding the container onto the piston rod while expanding and/or exposed to external forces.

Any type of fluid can be used that is a combination of compressible and non-compressible media, only compressible media, or only non-compressible media.
The change in the size of the container can be quite large from the smallest cross-sectional area that has a manufacturing size and is expanded with the largest cross-sectional area, so that the chamber in the container and the first enclosed space in the piston rod, for example, communication may be required. The first enclosed space can also be pressurized during changes in the volume of the chamber of the container in order to maintain the pressure within the chamber. Pressure management of at least the first confined space may be required.

FIG. 1A shows a longitudinal section of a chamber 186 with a concave wall 185 and the container 208 at the beginning (first longitudinal position within the chamber 186) and at the end of the stroke (second longitudinal position within the chamber 186). 208' and an expandable piston. The central axis of chamber 186 is 184. Container 208' exhibits its manufacturing size and has fabric reinforcement 189 within skin 188 of wall 187. During the stroke, the container wall 187 expands to a stop arrangement, which may be a textile reinforcement 189 and/or a mechanical stop 196.

Movement during the stroke is stopped outside the container 208 and/or another stop device. Thus, expansion of container 208 occurs. Depending on the pressure within chamber 186, longitudinal stretching of the container wall may still occur due to the pressure within chamber 186. However, the primary function of the reinforcement is to limit this longitudinal extension of the walls 187 of the container 208. During the stroke, the pressure within the container 208, 208' may remain constant. This pressure depends on the change in volume of the container 208, 208' and thus on the change in the circumferential length of the cross-section of the chamber 186 during the stroke. Also,
Pressure may change during the stroke. It may also be possible for the pressure to change during the stroke, depending on or independent of the pressure within the chamber 186.

1B shows the first embodiment of the expansion piston 208 at the beginning of the stroke.
is formed by a skin 188 of flexible material, for example of rubber type, with a woven reinforcement 189 that allows expansion. The orientation of the textile reinforcement with respect to the central axis 184 (= braid angle) differs from 54° 44'. The change in size of the piston during the stroke does not necessarily result in the same shape as depicted. Due to the expansion, the thickness of the container's wall may be less than the thickness of the container produced when placed at the end of the stroke (= second vertical position). An impermeable layer 190 may be present inside the wall 187. It is tightly squeezed to the top cap 191 and the bottom cap 192 of the container 208, 208'. Details of said caps are not shown, all kinds of assembly methods can be used. These can adapt to the change in thickness of the container's wall. Both caps 191, 192 can translate and/or rotate over the piston rod 195. These movements can be performed by various methods, for example by different types of bearings, not shown. The top cap 191 of the container can move upwards and downwards. A stop 196 on the piston rod 195 outside the container 208 limits the upward movement of the container 208. The bottom cap 192 can only move downwards as a stop 197 prevents upward movement, this embodiment is considered to be used for a piston-chamber device with pressure in the chamber 186 below the piston. In other types of pumps, e.g., dual acting pumps, vacuum pumps, etc., other stop arrangements are possible and depend only on the design specifications. Other arrangements for allowing and/or limiting the movement of the piston relative to the piston rod may occur. The adjustment of the sealing force may include a combination of an incompressible fluid 205 and a compressible fluid 206.

The walls 185a of the chamber 186 are parallel to the central axis 184 and are in an initial vertical position near the end of the stroke.
Chamber 209 within the container (both singly) may communicate with a second chamber 210 containing spring-loaded piston 126 within piston rod 195. Fluid can flow freely through the hole 201 through the wall 207 of the piston rod. The second chamber may be in communication with the third chamber (see FIG. 12), while the pressure within the container may also depend on the pressure within chamber 186. The container may be expandable through piston rod 195 and/or by communicating with chamber 186. O in the upper cap and the lower cap
Rings or similar 202, 203 seal the caps 191, 192 to the piston rod, respectively. Cap 204 is shown as an assembly threaded onto the end of piston rod 195. Similar stops can be placed at other locations on the piston rod depending on the required movement of the container wall. The contact area between the walls of the container and the walls of the chamber is 198.

FIG. 1C shows the piston of FIG. 1B at the end of the pump stroke, where the piston of FIG. 1B has its production size. The top cap 191 is moved a distance a' from the stop 196. Spring force actuated valve piston 126 has been moved a distance b'. Lower cap 192 is shown adjacent to stop 197 when there is pressure in chamber 186, and then lower cap 192 is pressed against stop 197. A compressible fluid 206' and an incompressible 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 is parallel to central axis 184. It is located in a second longitudinal position approximately at the end of the stroke.

FIG. 2A shows a longitudinal section of a chamber 186 with a concave wall 185 and an expandable piston including a container 217 in a first longitudinal position of the chamber and the same 217' in a second longitudinal position. shows. The container 217' shows its manufactured size with fiber reinforcement 219 in the skin 216 of the wall 218 due to a trellis effect. During a stroke, the wall 218 of the container is prevented from moving during a stroke by a stop device (which may be a textile reinforcement 219 and/or a mechanical stop 214 in the container and/or another stop device). Expand until it stops. This stops the expansion of the walls 218 of the container 217. The primary function of the fiber reinforcement is to limit the longitudinal extension of the walls 218 of the container 217. During the stroke, the pressure within the container 217, 217' may remain constant. This pressure depends on the change in volume of the container 217, 217' and therefore on the change in the circumferential length of the cross section of the chamber 186 during the stroke. It is also possible that the pressure changes.

During the stroke, it may or may not depend on the pressure in the chamber 186. The contact area 211 between the container 217 and the wall of the chamber is at a first longitudinal position.
2B shows a second embodiment of an expansion piston 217 at the beginning of a stroke.
is formed by a skin 216 of flexible material, for example of rubber type, with a fiber reinforcement 219 that allows the expansion of the container wall 218, so that the orientation of the fibers relative to the central axis 184 (= braid angle) differs from 54° 44'. Due to the expansion, the thickness of the container wall may be small, but not necessarily very different from the thickness of the container produced when placed at the end of the stroke (= second longitudinal position). An impermeable layer 190 may be present inside the wall 187. It is tightly squeezed to the top cap 191 and to the bottom cap 192 of the container 217, 217'. Details of said caps are not shown, all kinds of assembly methods can be used. These can adapt to the changes in the thickness of the container wall. Both caps 191, 192 can translate and/or rotate over the piston rod 195. These movements can be performed, for example, by
This can be done in various ways, such as with various types of bearings not shown. The top cap 191 can move up and down until a stop 214 restricts this movement. The bottom cap 192 can only move downwards, as a stop 197 prevents it from moving upwards. This embodiment is considered to be used for a piston-chamber device with pressure in the chamber 186. In other types of pumps, e.g., double-acting pumps, vacuum pumps, etc., other arrangements of stops are possible and depend only on the design specifications. Other arrangements for allowing and/or restricting the relative movement of the piston to the piston rod can occur. The adjustment of the sealing force may include a combination of incompressible fluid 205 and compressible fluid 206 (both can be alone) in the container, while the chamber 215 of the container 217, 217' can communicate with a second chamber 210 that contains a spring-force actuated piston 126 in the piston rod 195. The fluid can flow freely through the hole 201 through the wall 207 of the piston rod. The second chamber may be in communication with a third chamber (see FIG. 10), while the pressure in the vessel may also depend on the pressure in chamber 186. The vessel may be expandable through piston rod 195 and/or by communication with chamber 186. O-rings or similar 202, 203 on the upper and lower caps seal caps 191, 192 to the piston rods, respectively. Cap 204 is shown as a screwed assembly onto the end of piston rod 195.

Wall 185a of chamber 186 is parallel to central axis 184 and is located approximately at the end of the stroke at a first longitudinal position.
FIG 2C shows the piston of FIG 2B at the end of the pump stroke, where it has its production size. The cap 191 has been moved a distance c' from the stop 214. The spring force actuated valve piston 126 has been moved a distance d'. When there is pressure in the chamber 186, the bottom cap 192 is shown adjacent to the stop 197 than when the cap 192 is pressed against the stop 197. The compressible fluid 206' and the incompressible fluid 205', the contact area 211' of the container 217' and the wall of the chamber 186 at the second longitudinal position are shown.

Wall 185b of chamber 186 is parallel to central axis 184 and is located at a second longitudinal position approximately at the end of the stroke.
3A,B,C show an expandable piston including an initial reservoir 228 and a reservoir 228' at the end of the stroke. The production size is of the piston 228' at a second longitudinal position in the chamber 186. The construction of the piston may be the same as that of FIG. 7AJ3,C, except that the reinforcing bars may be bendable and may have any type of reinforcing bar means that may be in a pattern of reinforcing bar "pillars" that do not cross each other. This pattern may be parallel to the central axis 184 of the chamber 186, or one in which a portion of the reinforcing bar means may be in a plane that passes through the central axis 184.

3B shows the wall 218 with skins 222 and 224. Rebar 223. Contact area 225 between the container 228 and the wall of the chamber at a first longitudinal position. Impermeable layer 226.
FIG. 3C shows the contact area 225' between the container 228' and the wall of the chamber in a second vertical position.

FIG. 3D is a top view of pistons 228, 228', respectively, provided with reinforcing means 227, 227'.
FIG. 3E is a top view of pistons 228, 228', respectively, provided with reinforcing means 229, 229'.

4 shows a non-moving expandable piston 228' in a chamber 186 having walls 185a parallel to the central axis 184 of said chamber 186 in a position where the contact surface 225' between the piston 228 and the wall 185 of said chamber 186 is in a position where there is no pressure difference in the chamber between the two sides of the piston. The portion 185 to the first position of the chamber has an angle a with the central axis 184. A projection 1000 of the midpoint (center) 1001 of the elastically deformable wall of the piston on the central axis 184.

5A shows the piston of FIG. 4 momentarily stationary inside a chamber 186 with a conical wall 185 where the piston is beginning to expand, and the movable cab 191 is moving towards the non-movable cab 192. The contact surface 225'' has been increased and is located below each of the centers 1002 and 1003 of the elastically deformable wall of the piston and is a protrusion relative to each of the central axes 1004 (old) and 1005 (new). Distance f. Direction of movement 1006 of the movable cab 191. Force 1007 from the wall 187 of the piston to the wall 185 of the chamber 186. Distance g'.

Figure 5B shows the piston of Figure 5A, which is momentarily immobile and thereby expands, such that the contact area 225"' of the piston wall 187 with the wall 185 of the chamber 186 increases at a second longitudinal position of said contact surface 225"', the movable cap 191 being now immobile. The contact surface 225'' is around a point of the elastically deformable wall of the container with its midpoint (center). Centers 1008 (old) and 1009 (new) of the elastically deformable wall of the piston, i.e. its projections 1010 (old) and 1011 (new) on the central axis 184. Distance f. force 1012 from the piston wall 187 on the wall 185 of the chamber. Direction of movement 1013 of the force 1012. Movement 1014 of the movable cap 191.

FIG. 5C shows that the contact area 225'' of the piston wall 187 with the chamber wall 185 decreases at the second longitudinal position of said contact area, while the contact area 225'' of the piston wall with the chamber wall decreases in said contact area. 5B is shown expanding by being momentarily immobile to increase in first longitudinal position. The centers 1015 (old) and 1016 (new) of the piston's elastically deformable walls are respectively Its protrusion 1017 (old) and 1018 (new) on the central axis 184. Distance g'. Direction of movement 1019 of the reaction force 1020 of the chamber wall 185 on the wall 187 of the piston. Direction of movement 1021 of the wall 187 of the piston. .

FIG. 5D shows the piston of FIG. 5C, where the non-movable cap 192 starts to move instantaneously from the second longitudinal position to the first longitudinal position, thereby moving the piston in the same direction. The contact area 225"" is much smaller than 225"" in FIG. 5C. Distance h'. Protrusion 1022 of the center 1023 of the elastically deformable wall of the piston on the central axis 184. Direction of movement 1024 of the movable cap 191, direction of movement 1025 of the non-movable cap 192 and therefore of the entire piston. Leakage 1026 occurs at that point.

FIG. 5E shows the piston of FIG. 5D in which piston movement is reduced due to an increase in contact area 225. A protrusion 1027 on the central axis 184 of the center 1028 of the elastically deformable wall of the piston. Movement direction 1029 of movable cap 191. Piston wall movement directions 1030 and 1031.

FIG. 6A shows an expandable piston 898 moving 900 in engagement or sealing within a cone-forming chamber 899 with a reinforced (not shown) wall 901 embedded within a stationary cab 903 and a movable cab 904 . The cab 904 is slidably movable on a hollow piston rod 902 that forms a sealed space, and communicates with the space within the piston 898. A fluid or mixture of fluids is present within the piston. Said chamber is closed with spaces 906, 907 on either side of the piston and may contain a fluid or a mixture of fluids on one or both sides of the piston 898. Contact area 905 between wall 901 of piston 898 and wall 897 of chamber 899. The presence of fluid on both sides of the piston may cause the piston to move in a different manner than desired.

6B shows the piston 898 of FIG. 6A moving in engagement or sealing within a conically formed chamber 896 having spaces 908 and 909 on either side of the piston 898. In the wall 895 of the conically formed chamber 896, a tube 911 at a first longitudinal position allows communication between the space 908 and the surrounding atmosphere 910, while a tube 912 is assembled within the wall 895 of the conically formed chamber 896 and allows communication between the space 909 and the surrounding atmosphere 910. Contact area 905
is between the wall 901 of the piston 898 and the wall 897 of the chamber 896. 910 is the surrounding atmosphere.

Fig. 6C shows the piston 898 of Fig. 6A moving in engagement or sealing within a conically formed chamber 894 having spaces 908 and 909 on either side of the piston 898. The wall 893 of the conically formed chamber 894 has a tube 913 at a first longitudinal position which allows communication between the inside of a tube 915 and the space 908, which tube 915 communicates with a tube 914 which is assembled within the wall 893 of a conically formed chamber 896 and communicates with the space 909 of said conically formed chamber 894. A contact area 905 between the wall 901 of the piston 898 and the wall 893 of the chamber 896.

FIG. 6D shows piston 892 moving into engagement with a conical chamber 899 having spaces 906 and 907 on each side of piston 892. The spaces 906 and 907 communicate with each other via tubes 918 assembled within the cabs 891 and 890, respectively. Contact area 905 between wall 901 of piston 898 and wall 897 of chamber 899.

FIG. 6E shows a piston 898 engaged and movable within a conical chamber 899. This chamber is closed with spaces 906, 907 on either side of the piston and may contain a fluid or a mixture of fluids on one or both sides of the piston 898. There is no contact area between the inner wall 922 of the cone-forming chamber 899 and the outer wall 923 of the piston 924; instead, a gab 920 exists between said walls 922 and 923, and fluid 921 is directed to the movement 900 of said piston 898. allows flow in the opposite direction.

FIG. 6F shows an actuator piston 925 based on the piston 924 shown in FIG. 6E, with ducts 926. Preferably, three ducts 926 are spread evenly over the contact area 927 of the wall 928 of the actuator piston 925 and the wall 922 of the chamber 899. The ducts 926 allow fluid communication between both spaces 906 and 907 of the chamber 899. The part 929 of the contact area 927 that is in sealing contact with the wall 922 of the chamber 899 along the periphery is smaller than in the absence of said ducts 926, and the resulting drive force of said actuator piston 925 is still acceptable. The length of said ducts 926 in the longitudinal direction is greater than the longitudinal direction of the contact area 927 in order to obtain communication between said spaces 906 and 907 of the chamber 899 in all longitudinal positions. Piston rod 929. Movable cab 930.

FIG. 6G shows a cross-section of the piston rod 929 of FIG. 6F and a view on the actuator piston 925 from a first longitudinal position. Chamber wall 922. Movable cab 930. The duct 926 raises the circumference of the actuator piston 925 approximately equally 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 a pump stroke. The walls of the chamber are parallel to the central axis 184, which is why the reservoir does not move when pressurized.

FIG. 7B shows the piston of FIG. 7A in a portion of the chamber where the walls are not parallel to the central axis but at a positive angle. The piston moves toward the first position because the center point of its flexible wall is above the contact surface with the wall.

FIG. 7D is a three-dimensional view showing a reinforcing matrix of fibrous material that allows for elastic expansion and contraction of the walls of the containers 208 , 208 ′ as they move confined within the chamber 186 .
The woven material may be elastic and may be placed in separate layers from each other. These layers may also be woven together. The angle between the two layers may differ from 53°44'. If the type and thickness of the material is the same for all layers and the number of layers is equal, the expansion and contraction of the container wall may be equal in the XYZ directions while the seam size in each direction is equal. When the seams ss, tt are stretched, they become larger in each direction of the matrix, respectively, and when they are contracted, they become smaller. Since the material of the thread may be elastic, another device to stop the expansion may be required, such as a mechanical stop. This may be a mechanical stop shown on the wall of the chamber and/or on the piston rod, as shown in Figure 7B.

FIG. 7E is a three-dimensional view showing the reinforcement matrix of FIG. 7D unfolded. Seams ss' and tt'
is greater than the seams ss and tt. Shrinkage can result in the matrix shown in FIG. 7D.

FIG. 7F is a three-dimensional view and shows a reinforcing matrix of woven material made of inelastic threads (elastically bendable) and superimposed on each other in separate layers or woven together. Expansion is possible due to the extra length of each loop 700 that is available when the container is in production size and also pressurized when placed in the second longitudinal position of the chamber. The seams ss, tt in each direction may limit the maximum expansion of the wall 187 of the container 217 if the container wall is expanding inelastic material. For example, it may be necessary to stop the container 217 from moving over the piston rod 195 by a stop 196, so that a sealing remains. The absence of such a stop 196 may give the possibility of forming a valve.

Figure 7G is a three-dimensional view showing the reinforcement matrix of Figure 7F expanded. Stitch ss' and tt' contractions larger than seams ss' and tt' may result in the matrix shown in Figure 7F.
FIG. 8 shows a piston combination comprising an elastically deformable container 372 moving within a chamber 375 within a cylinder wall 374 and a tapered wall 373 shown, for example, centered around a central axis 370. The piston is suspended on at least one piston rod 371. The containers 372, 372' are shown in a second longitudinal position of said chamber (372') and in a first longitudinal position (372').

All solutions disclosed herein can also be combined with a piston type, where a chamber with a cross section with constant circumferential dimensions can be a solution to the obstruction problem.

Figure 9A shows a longitudinal section of a chamber with a convex/concave wall 185 and an expandable piston containing an initial container 258 and the same 238' at the end of the stroke. Container 258' indicates its production size.

FIG. 9B shows a longitudinal section of a piston 258 with a wall 251 and a reinforced skin 252, in which at least an elastically deformable support member 254 is rotatably fixed to a common member 255 and connected to the skin 252 of said piston 258, 258'. These members are in tension and have a certain maximum extension length depending on the hardness of the material. This limited length limits the extension of the skin 252 of said piston. The common member 255 can slide on the piston rod 195 by means of sliding means 256. The rest is of a structure comparable to that of the pistons 208, 208'. The contact area 253.

FIG. 9C shows a longitudinal section of piston 258'. Contact area 253'. FIG. 9D shows a longitudinal section of a piston 258'' with a common area 253''. Center 1020 of the elastic deformation wall 251 of the piston. Center axis 1022
Projection of the center point 1020 above.

10A to 10F illustrate the pressure arrangement of a combination of inflatable actuator pistons running in a chamber, said chamber having a cross-sectional area of different cross-sectional areas and different circumferential lengths in first and second longitudinal positions. having at least a substantially continuously different cross-sectional area and circumferential length at an intermediate longitudinal position between said first and second longitudinal positions, said second longitudinal position wherein the cross-sectional area and circumferential length are less than the cross-sectional area and circumferential length at the first longitudinal position, and the actuator piston moves from the second longitudinal position to the first longitudinal position. During the extension, the volume of the enclosed space remains constant. This is done with both techniques (CT and ESVT).

10G-L (inclusive) show a pressure arrangement of a combination of an expandable actuator piston traveling in a chamber, the chamber having a cross section with different cross-sectional area and different circumferential length at a first and a second longitudinal position, and at least substantially continuously different cross-sectional area and circumferential length at intermediate longitudinal positions between the first and the second longitudinal positions, the cross-sectional area and circumferential length at the second longitudinal position being smaller than the cross-sectional area and circumferential length at the first longitudinal position, and the size of the confined space is reduced when the actuator piston travels from the second longitudinal position to the first longitudinal position. This is done to reduce the volume of the pressurized medium and thus the energy used to recompress the medium. This can be preferably done in embodiments using ESV technology, because changing the size of the closed space volume is easier to do than in embodiments using consumption technology.

FIG. 10A shows a piston-chamber combination with a chamber 186 having a centerline 184 with a wall 185 of the chamber 186, which is described in Section 207 of this patent application.
, 653, 19660 and 19680, a pressurized elliptical piston 217' moves 2003 from a second longitudinal position 2000 to a first longitudinal position 2001. In said first longitudinal position 2001, the piston 217' has a fixed volume of sealed space 210 while expanding into a piston 217 having a spherical shape. This means that the pressure in said piston 217 gradually decreases during the movement 2003 and is at its lowest value at the first longitudinal position 2001. Also, the shape of the piston 217 in said first longitudinal position may be an ellipsoid (not shown) as described and shown in § 19660 of this patent application, which reduces the increase in pressure in said piston. The position 2004 of the valve 126 does not change during said operation, so the volume of the sealed space 210 does not change. Arrow 2005 indicates that the next stage of operation is shown in Figure 10B or 10C and is finally indicated by arrow 2011. Position 2025 shows piston 217' in a second longitudinal position where the wall is present.

2030 of the chamber 186 is parallel to the central axis 184. The position 2026 of the piston 217 in a first longitudinal position where the walls 2031 of said chamber 186 are parallel to the central axis 184. Shape 2027 shows said piston 217 when it starts depressurizing (delayed) in a first longitudinal position. The shape and size 2028 is when the piston 217'' is about halfway through its return stroke and is slightly separated from the wall 185 of the chamber 186 due to delayed decompression. The same shape and size 2028 of the piston 217' is , the piston 217'' is engaged (not free) with the wall 185 of the chamber 186, so that the piston 217'' is closer to the second longitudinal position than when it is moving to the second longitudinal position ( distance y).

The size of the enclosed space under valve 126 is determined by the length of the channel to the bottom of the piston rod. The length is "a" at the second longitudinal position and "b" at the first longitudinal position, where a = b.

FIG. 10B shows the valve 126 moved further away from the piston 217 from its position 2004 to a position 2007.
(2006). 210' is a closed space. As a result, the volume of the enclosed space 210' is reduced, the pressure within the piston 217'' is approximately the same as the pressure at which said piston was created (e.g., atmospheric pressure), and its size and shape 2 longitudinal position 2000, but is now approximately the same size and shape as it is when unpressurized. This is because when returning from the first longitudinal position 2001 to the second longitudinal position 2000 ( 2008), meaning that the piston 217'' may engage and/or disengage the wall 185 of said chamber 186, but may not seal. 2024 is the wall of the piston.

When the piston 217" is moving (2008) from the first longitudinal position 2001 to the second longitudinal position 2000, an internal pressure drop is obtained relatively slowly, and for this reason the piston 217B" during this movement can have a more elliptical shape than the shape of 217' at the second longitudinal position 2000, so that the piston 217B" during this movement engages and/or does not engage with the wall 185. In comparison, the same size of the piston 217B" is obtained further away to the second longitudinal position than when the piston is moving (sealing and/or engaging) 2003 from the second longitudinal position 2000 to the first longitudinal position 2001. The pressure drop may already be obtained at the first longitudinal position 2001.

When the pistons 217", 217B" return to the second longitudinal position 2000, the position of the valve 126 within the closed space 210' changes from 2007 to 2004, and the closed space 210' returns to its original volume in Figure 10A again. , so that the piston 217' has its original pressure again. Arrow 2010 indicates the next step in the operation shown in FIG. 10A.

FIG. 10C illustrates an alternative solution for varying the internal pressure of piston 217 and is to be considered in conjunction with FIG. 10A. In this case, valve 126 is missing and instead there may be an inlet/outlet arrangement 2020. See, for example, FIGS. 210A-F (inclusive) and 211A-F (inclusive) of Article 653 of this patent application. Pressurized piston 217' moves 2003 from second longitudinal position 2000 to first longitudinal position 2001 as depicted in FIG. 10A. Confined space 210
No addition or removal of fluid from the sealed space 210 occurs. Arrow 2011 indicates the next phase of operation in FIG. 10C. Depressurization of the piston 217" is obtained by removing the required amount of fluid from the sealed space 210. When said piston 217" is moved back from the first longitudinal position 2001 (arrow 2021) to the second longitudinal position 2000, sufficient fluid is added to the sealed space 210 (arrow 2022), resulting in piston 217'" (arrow 2023), the next phase is shown in FIG. 10A, piston 217'. The walls 2024 of the piston 217" are then pressed against the piston 217'.
It should be emphasized that the combination of both above techniques may be an additive solution for pressure management of the pistons. It is possible that the pressure drop from the piston 217 or 208 to the piston 217" or 208", respectively, may be gradual, e.g. computerized, provided that the wall 2024 of the piston is engaged with the wall 185 of the chamber 186 during the return from the first longitudinal position 2001 to the second longitudinal position 2000.

Walls 185 of chamber 186 in Figures 10A-10L have second and first longitudinal directions.
The position may not be parallel to the central axis. There are no channels as shown in Figures 4 and 5A-E (inclusive).

Figures 10D-10F show an analog process to that shown in Figures 10A-10C, with a spherical piston 208.

Figures 10G-I show an analog process to that shown in the figures. In 10A-C, the difference is that more pressure can be maintained when the piston 217? is moving from the second longitudinal position 2000 to the first longitudinal position 2001, as shown in Figure 10A, and the valve 126 is not removed as much from the bottom end of the piston. The length of the piston rod below the piston 126, giving the size of the volume of the enclosed space, is "e", but between the second and first longitudinal positions this length decreases to "f", and in the first longitudinal position this length further decreases to "g", where e > f > g.

Figures 10J-L show processes comparable to those shown in the figures. Pressure is maintained as described in FIG. 10G, but now with a spherical piston 208 10D-F. The length of the piston rod under the valve 126, which gives the size of the enclosed space volume, is "h",
Between the second and first longitudinal position this length is reduced to 'i' and in the first longitudinal position this length is further reduced to 'j', where h > i > j.

The process called E (enclosed) S (pace) V (volume change) T (technique) is shown in the figure. Figure 10A, 10B
10D, 10E are used in the motor according to the present invention. 11F, G (crankshaft) and 13F, 13G, 14A to H (rotation) in the diagram.

The process called C (onsumption) T (technology) shown in Figs. 10A, 10C or Figs. 10D, 10F and Figs. 210A-F (inclusive) and Figs. 211A-F (inclusive) is used in a motor according to the invention and is shown in Figs. 11 A-C (inclusive) (crankshaft) and Figs. 12A-C (inclusive), 13A-D (inclusive)
Figure 10M shows the BB section of Figure 12C (and said BB section may be partially shown in Figure 12A) and a motor with the piston of the actuator piston-chamber combination moving but the chamber not moving. The motor with chamber 960 comprises four sub-chambers 961, 962, 963, and 964 each located successively to one another about the same central axis 965 having axis 966 through the center 967 of the chamber 960. In each of the sub-chambers 961, 962, 963 and 964, a piston 968 is arranged and is shown in two key positions, namely in position 968' when in a first rotational position of the sub-chamber 964 having the largest diameter and in position 968" when in a second rotational position of the sub-chamber 961 lying in succession with the sub-chamber 964, so that the first rotational position of the sub-chamber 964 is closest to the second rotational position of the sub-chamber 961 having the smallest diameter. The actuator piston 968 rotates clockwise around the actuator piston 966 and four holes 970 for assembling the chamber 960 to the axle 966 are shown.

FIG. 10N shows the BB section of FIGS. 13A and 13B, and the motor is of the type where the chamber of the actuator piston-chamber combination moves and the piston does not move.
A motor with a chamber 860 comprises four subchambers 861, 862, 863 and 864, respectively, located in series with each other and around the same central axis 865, with an axis 866 through the center 866 of the chamber 860. Five pistons 868, 869, 870, 871, and 872 are arranged in the subchambers 861, 862, 863, and 864, respectively, and each piston 861, 862, 863, and 864 is at a different rotational position. , placed at an angle a = 72°. Each piston is
Includes piston rods 873, 874, 875, 876, and 877. Piston 868, 869, 870, 871,
and 872 are shown to be "spherical" in shape, all having different diameters. The chamber 860 includes a subchamber 861 having the axis 866, a second rotational position, and a first rotational position.
, 862, 863, and 864, and four holes 878 are shown for assembling the chamber 860 to the shaft 866.

The motor according to Figures 10G and 10H may include a chamber 860, at least a portion of which may be parallel to the central axis of the chamber (not shown).
A circular chamber with identical subchambers can have an actuator piston in each subchamber, with all actuator pistons located at the same circular point in each subchamber.
19615 Amendment - For pressure management systems in Figures 11F, 13F and 13E This relies on a system of bi-directional actuators (e.g. Figure 11F refs. 1056 and 1057), where a change in direction causes a loss of pressure. may be caused by a "consumption" of the fluid, if a repressurization system is required, or if the fluid during a change of direction may be restarted to the atmosphere; It can also be caused by pressure drop. See Figure 13E. The reassurance mechanism is similar to that shown in the previous drawing. For example, fig. 11A, 11B and Figure 12A.

It is also possible to develop systems that do not "consume" fluid, but in some cases only "consume" pressure. In Figures 11F, 13F, only a pressure storage vessel of constant volume is required since it is assumed to already exist. The pressure is preferably low pressure (e.g. 10-15 bar)
, optionally at high pressure (eg 300 bar).

The system may comprise a classic cylinder in which a bidirectional piston is placed. On each side of the piston, the cylinder has an inlet and an outlet valve, so that the inlet valve on one side communicates with the outlet valve on the other side of the piston. The sum of the accumulated volumes on both sides of said piston may therefore return to a constant, which leads to the fact that it is possible to move the piston from one side of said cylinder to the other without consuming fluid. Both pressures are consumed. This means that for example there is only power present to control said valves, which can very well be obtained from a sustainable source of power, for example a photovoltaic cell, for example a storage battery loaded by a generator that can be connected to the bolt and/or the main shaft. This allows to further reduce the energy required for this motor. We assume that the pressure storage vessel was loaded at the production of the motor.

Instead of a bidirectional actuator, an electric step motor controlled by a computer can be used. Such a motor can respond accurately and quickly to controlling impulses from the computer.

Alternatively, the system shown in references 1093 and 1094 in FIG. 13F may be used here.
Addition to the description of the preferred embodiment of FIG. 11F The holes of the piston rod 805 in the reservoir piston 810 are not shown in the reservoir piston 810, but they are already shown in the figures. 2B, 2C, and reference 201 should be present in FIG. 11F.
Addition to the description of the preferred embodiment of Fig. 13F The holes for the piston rod 805 in the reservoir piston 810 are not shown in the reservoir piston 810, but they are already shown in the figure. 1B, 1C, datum 201 should be present in Fig. 13F. Regarding the pressure management system of Figs. 11A, 11B, 11C Regarding the actuator piston (Figs. 11A, 11B, 11D) connected to a main shaft by a crankshaft, where the fluid in said actuator piston is depressurized and then pressurized by a system in which the space within the piston is sequentially connected and disconnected to a recompression pump and a pressure storage vessel, the following remarks are made.

Immediately after reaching the turning point at the furthest second longitudinal position, when the depressurized actuator piston moves from the first longitudinal position to said second longitudinal position, there is a communication between the pressure vessel (e.g., FIG. 11B - reference number 314) and the actuator piston, which is immediately pressurized when the piston was at the furthest second longitudinal position. At that point, there is an open connection between said pressure storage vessel through the second enclosed space of the crankshaft and the enclosed space of the piston rod, and the hole of said piston rod in the vessel through the two holes of the crankshaft and the connecting rod, which is a continuous communication between the space in said vessel and said enclosed space.

This is because during the stroke from the second longitudinal position to the first longitudinal position, the sealed space of the piston temporarily has a constant volume, which is the result of the volume of the container increasing (
This means that as the container moves from an ellipsoid with a smaller circumference to a sphere/ellipsoid with a smaller diameter to a sphere with a larger diameter, the internal pressure within the container decreases continuously.

Furthermore, it is possible that the internal pressure of the container had decreased upon reaching the first vertical position.
It is possible that atmospheric pressure had not been reached. When returning to the second longitudinal position, the space within the container, the hole between said space and the closed space of said container in the piston rod, and the connecting rod immediately before or in the immediate vicinity of the furthest first longitudinal position. A third closed space in the crankshaft can communicate through two holes, one in said connecting rod and one in the crankshaft, at that point. have a corresponding central axis.

A pump communicates with the third enclosed space and draws fluid from the container at that point;
The vessel is depressurized.
The second enclosed space may be constantly pressurized by being in continuous open communication with a pressure reservoir, and this connection may be controlled by a valve.
Added to the description of the preferred embodiment of Figures 11A, 11B, and 11C.

The holes for the piston rod 805 in the reservoir piston 810 are not shown in the reservoir piston 810, but they are already shown in reference 201 in Figures 2B and 2C and should be present in the figures.
Regarding the Pressure Management System of Figures 12(A), (B), (C), (C), (C), (C), (C), (C), (B) In the case of a circular chamber having a circular central axis and the same pressurization system as described above for the crankshaft solution (Figures 11A, 11B, 11D), a similar solution may be effective in said circular chamber, although in a slightly adapted manner.

In the case of a movable piston and a non-movable chamber (FIGS. 12A, 12B, 12C), the spherical piston communicates through a hole in the piston rod, through a space in the container, and at the other end with a second sealed space that may be located in the main shaft, which may comprise a sealed space. The above may communicate with a two-way valve in the housing, which may be constructed around the main shaft. The separator valve may be a T-valve, whose shared part communicates with the second sealed space. One of the non-shared parts may communicate with a pressure storage vessel (e.g., reference number 814) (high pressure) and the other (low pressure) with a pump (e.g., reference number 818). The control of how the separator valve is opening and closing may be done by a computer, which monitors the position of the main axle compared to the opening of the closed space and the opening of the second closed space in the main shaft. It may also be done by a camshaft communicating with the main shaft. Because in the figures the number of single chambers is 4. 12A and 12B are
There should be four outlets/inlets to the second closed space in the main shaft, and there should also be four outlets/outlets to the T-valve. Between the T-valve (low pressure end) and the pressure storage vessel (e.g. reference 814), a pump (e.g. reference 818, 826) may be added so that the pressure is a little higher than the pressure in said pressure storage vessel. All this makes this solution less than optimal, for example the transition from the second closed space to the second closed space in the main shaft may cause leakage.

If the piston is stationary and the chamber is moving (Figures 13 A, 13B), for example, each of the subchambers has the same central circumferential axis, and all subchambers are placed in series with each other and There may be five pistons in communication. Each piston is in communication with a T-valve as described above, as if the piston were moving and the chamber was not. Also,
The pressurization system can be as follows.

Similarly, the only difference is that there are five T-valves, each with a different piston position in the same subchamber, and therefore may be opening and closing at different times.
Instead of a piston pump, a centrifugal pump may be used (Figure B). The efficiency of a centrifugal pump may be lower than that of a piston pump with a conical chamber.
Addition to the description of the preferred embodiment of Figures 12A-12C, 13A-13F The holes of the piston rod 805 in the reservoir piston 810 are not shown in the reservoir piston 810, but they are already shown in the figures. 1B, 1C, Reference 201 should be shown in Figures 12A-C, 13A-F.
Addition to the description of the preferred embodiment for FIG. 12C.

A return channel 1150 from 1074 to the pump 1151 has its outlet connected by channel 1152 to the storage pressure vessel 1075. The pump 1151 may be connected to the main shaft 966 and/or an external sustainable energy source such as solar power (not shown).

Added to the description of the preferred embodiment of FIGS. 12A-12C (inclusive) and FIGS. 13A-13F (inclusive).
The holes in the piston rod 805 in the container piston 810 are not shown in the container piston 810, but these are already shown in the figure. 1B, 1C, reference 201 should be shown in the figure. 12A-C, 13A-F.

Additions to the description of the preferred embodiment for figures. 13A, 13B, 13E.
Valve body 1160 provides communication [829] from pressure storage vessel 814 to each piston 868, 869, 870, 871, 872 (see Figure 13C) via piston rods 873, 874, 875, 876, 877, or For the channel [817] to the repressurization pump 818 and indirectly to the channel [817] to 826 and/or the pressurized return channel [825] and/or from said pump to the pressure storage vessel 889. 828] are equipped with 5x T-valves 1161 to 1165 (inclusive) that are open for.

Return channel 1150 from 1074 to pump 1151 is connected at its outlet by channel 1152 to storage pressure vessel 1075. Pump 1151 may be connected to a main shaft 966 and/or an external sustainable energy source such as solar power (not shown).
19627- - Based on 19618- - Figures 11A-Z updated based on 19617- (Main document 19601)
FIG. 11A schematically shows the overall system for an all-demand compatible (“green”) motor, as described in the Background of the Invention. A generally elongated crankshaft 800 having a U-shaped axis 801 is provided with a piston rod 805 assembled with bearings 802, 803 and a contraweight 804, on the opposite side of the piston rod 805. is connected to an expandable piston 806. The piston rod is shown left "L" in movement from a first longitudinal position to a second longitudinal position (with an arrow) and from the second longitudinal position to the first longitudinal position.
The right "R" is shown in the longitudinal position of the movement (with arrow). The piston 806 is engageably movable within the chamber 807 with the inner wall 808. Said chamber 807 has a cross-section with successively different cross-sectional areas and different circumferences, and its inner wall 808 has a circumference in a second longitudinal position that is smaller than in the first longitudinal position. The piston 806 is manufactured to a production size of its unstressed circumference to be approximately the dimension of the circumference of the wall 808 of said chamber 807 in a second longitudinal position. The piston 806 is connected to the piston rod 805 by a cap 809, while the flexible wall 810 of the piston 806 is provided with reinforcing means 811 and a slidable cap 812 that can slide over the piston rod 805. is connected to the piston rod 805 by. The piston 806 is positioned in a second longitudinal position and communicates with a pressure source, e.g. When 806 is pressurized by fluid 822, the piston 806 begins to move from the second longitudinal position to the first longitudinal piston position, thereby causing the U-shaped axis 801 to align with the bearings 802 and 803. rotate around it. Said movement changes the direction of movement of said piston 806 in the opposite direction, ie from a first piston position to a second longitudinal piston position. The closed space 813 of the piston 806 is then connected to a piston pump 818 (which may alternatively be a rotary pump, e.g. a centrifugal pump) within the crankshaft 800 (shaft 801) via a channel [817]. It communicates with a third sealed space 816 of , is connected to a crankshaft 820 by a piston rod 819 , and has a U-shaped shaft 821 . Crankshaft 820 may be connected to crankshaft 800 so that rotation of U-shaped axle 801 causes rotation of said U-shaped axle 821 with contra weight 834 to the motor. Said communication reduces the pressure of fluid 823 within said piston 806 and thus reduces the circumference of wall 808, thus moving said piston 806 from a first longitudinal piston position to a second longitudinal piston position. Can be moved. Fluid 823 is at reduced pressure (relative to the pressure of fluid 822 when the piston is pressurized in the first longitudinal position) and is then pressurized by said pump 818 to fluid 827 (its pressure is (of course less than the pressure of the fluid 822), optionally transported directly to said pressure vessel 814 through a channel [824] or preferably transported to another piston pump 826 by a channel [825]; The fluid 827 is then pressurized to the fluid 822 in the pump 826 and then transported to the pressure vessel 814 through the channel [828].
It is also possible to repressurize the pressure storage vessel 814 via a hose 2701 communicating with a pressure source. From the pressure vessel 814, the fluid 822 is transported through the channel [829] to the second enclosed space 815. Piston pump 826 is electrically driven by motor 830 via another crankshaft 831. The motor 830 may be connected by a wire [1069] to an electrical storage device, such as an accumulator (or capacitor ("capacitor") storage type) 832, which is connected to a solar cell 833, for example. Electric motor 830 can be used as a starting motor for the rotation of crankshaft 800. This can be done by clutch 836 (not shown). Crankshaft 800 may be connected to a flywheel 835 (not shown) and a gearbox 837 (not shown), which gearbox 837 may use hydrodynamic bearings to reduce friction. good. Bearing 833 of crankshaft 821 of piston pump 818. Alternator 850 is in communication with main shaft 852 and charges battery 832 via connection 842. 15A, 15B, 15C or 15E. This battery 832 can also be charged by external power source 2700, for example via a cable.

FIG. 11B schematically shows a control device for the motor of FIG. 11A. Electric starting motor 830 includes a clutch (not shown) to connect axle 831 and/or 852 to the electric motor's anchor when the motor needs to be started. An electrical switch 838 can turn the starter motor 830 on and off by connecting to a battery (“accumulator”) 832 that is loaded by a solar cell 833. The motor 830 can also be stopped if the pressure in the pressure vessel 814 meets a certain maximum limit and the pressure measurement is performed by a pressure sensor 839.

The motor can also be started without using the starter motor 830, simply by opening the pressure reducing valve 840 in the channel [829]. Opening this deceleration valve 840 further upward causes the crankshaft 801 to rotate faster, and screwing the deceleration valve 840 downward causes the crankshaft 801 to rotate more slowly. Closing pressure reducing valve 840 completely stops the motor. Speeder 841 is in communication with deceleration valve 840. Alternator 850 is in communication with main shaft 852 and charges battery 832 via connection 842. The configuration 851 of the auxiliary power source is shown in the figure. 15A, 15B, 15C or 15E.

11A to 11F relate to a motor having an elongated cylinder and a piston communicating with a crankshaft, according to consumption technology.
FIG. 11C is a diagram illustrating the actuator piston pressure management of FIGS. 11A and 11B. Once the piston has arrived from the first longitudinal position in the final second longitudinal position of the chamber - thus immediately after reversing the direction of movement of the piston - the pressurized first position of said crankshaft 2
Communication between the closed spaces 822 of the piston rod begins through a hole in the crankshaft and through a hole in the end of the piston rod with a closed space in the piston rod, so that through the internal volume of the piston, the piston moves up to maximum pressure velocity. It becomes pressurized. Due to its pressurization, the piston begins to move to a first longitudinal position, thereby rotating the crankshaft and closing said hole, so that said communication is stopped. Said movement is reducing its internal pressure due to the increase in its internal volume due to the fact that the oval-shaped piston begins to deform into the shape of a sphere. When the first longitudinal position is reached, a moderate pressure remains within the piston and a sealed space within the piston rod still exists. The piston is the second
Upon reaching the first longitudinal position of the primo on the way back to the longitudinal position of , and begins to communicate with a third enclosed space 823 within the crankshaft that includes a hole. As the pressure within the piston and in the enclosed space decreases to a certain minimum value (eg, atmospheric level), the shape of the piston changes from a sphere to an ellipsoid. Due to the inertia of the crankshaft (or the driving force of another piston-chamber combination using the same crankshaft), the retracted piston moves to a second longitudinal position and the process begins again.

By means of communication between the enclosed space of said actuator piston and the second and third enclosed spaces within the crankshaft, the pressurized fluid must reach the piston so that it can be moved again by opening the pressure reducing valve. The piston can be stopped at a predetermined longitudinal position so that the piston can be stopped at a predetermined longitudinal position. This can only be a problem if there is only one actuator piston-chamber combination on one axis crankshaft. In this case, the piston may stop in the first longitudinal position and return a little on the way to the second longitudinal position for the following reasons.

Inertia The holes in the closed space may not be able to communicate with each other and starting may only be possible by using a starter motor.
The pressure drop in the piston may be caused by a suction in the third closed space 823, caused by the piston pump 818 taking in fluid from the channel [817]. The pressure drop in the channel [817] may begin a little before the actuator piston reverses its direction of movement from approaching the first longitudinal position to the second longitudinal position, so that fluid is sucked out of said closed space of the actuator piston when said holes in the closed space and the third closed space open. 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 be different from zero. The main shaft 852.

Details of the assembly of piston rod 805 and U-bend axle 801 are shown in Figure 11D. Details of the junction of piston rod 805 and connecting rod 925 are shown in Figure HE. Details of the assembly of piston rod 819 and crankshaft 820 of pump 818 are shown in Figure 11T. Details of the guides for connecting rod 925 and piston rod 819 are described in Section 19597 of this patent application.

As another preferred detail, preferably two valve actuators are connected with each other from the second enclosed space 822 of the crankshaft 800 to the space 813 of the piston rod 805 according to FIG. 210F or optionally according to FIG. 210E. a combined assembly comprising a check valve, preferably according to FIG. 210F, or optionally comprising a valve actuator according to FIG. 210E, from the space 813 of the piston rod 805 to the third enclosed space 823; The same assembly may exist. There may also be two separate assemblies, each comprising a check valve 522 with a subassembly 520 comprising a valve actuator according to FIGS. 304 and 301, one in the second enclosed space of the crankshaft 800. 822 to the space 813 of the piston rod 805, the same assembly comprising a check valve 522 in the opposite direction, and a subassembly 520 comprising the valve actuator according to FIGS. 304 and 301 from the space 813 of the piston rod 805. up to the third enclosed space 823.

11D shows the assembly of piston rod 805 and U-bend axle 801 of FIG. 11C at a point where piston rod 805 and U-bend axle 801 are shown inverted relative to each other. U-bend axle 801 assembled with piston rod 805 along with bearings 1100, 1100', 1100"", and O-rings 1104, 1104', 1104"", and 1104'" between piston rod 805 and axle 801. Closed space 813 is in through communication (with fluid 823) with third closed space 816.

(Currently) Hole 1102. The second closed space 815 with fluid 822 is in communication with the current blind hole 1101 and is therefore currently not in communication with the closed space 813. Separator 1103 separates second closed space 815 and third closed space 816. At another point, current hole 1102 becomes a blind hole, while current blind hole 1101 becomes a hole. The holes 1101 and 1102 do not communicate with the closed space 813 at the same time. Base 926 of piston rod 805
includes two portions 927 and 928, and the central axis 929 of channels 822 and 823 extends from said base 926.
within the separation plane (not shown). Two bolts 930 and a ring 931 on either side of the piston rod 805 hold the two parts 927 and 928 together.

Figure HE shows details of the joint between piston rod 805 and connecting rod 925 (805') shown in Figure 11C. The piston rod 805 has an end 932 that connects the second enclosed space 815 and the third enclosed space 816 on one side and the enclosed space of the piston 810 on the other side. A channel 933 is provided that communicates with the space 813. Both closed spaces communicate with each other via a space 941 between a hole 945 in the outer wall 943 of the end 932 of the piston rod 805 and a hole 946 in the inner wall 944 of the connecting rod 925. End 942 of connecting rod 925 includes an O-ring 939 sealing said end 942 to said end 932 of said piston rod 925. The shaft 940 is firmly connected (does not move) to the end 932. End 932 of piston rod 805 is comprised of two sections 934 and 935 that are bolted together by bolts 936 and washers 937, one on each side of centerline 938 of the assembly. Connecting rod 925 may overturn end 947 of said shaft 940. The end 947 has an increased diameter relative to the diameter of the shaft 940 to form a shoulder 953. Parts 934 and 935 of end 925 have 90° bearings 948 that are bearings for movement of end 942 over end 932. An O-ring 950 seals the shaft 940 over the bore 947 of the connecting rod 925.

FIG. 11F shows details of the U-shaped shaft 801 and the channels (e.g. 823) inside said crankshaft, as shown in the figure. 11A-C The channels 823 may be drilled during the manufacturing process of the crankshaft 801 after a temporary hole is made by forging. This drilling leaves holes in the outer wall 952 of the crankshaft 801, which can be closed by any means such as welding rods, sealed screws, etc. The figure shows a pin 954 with a head 955, which fits very finely into a hole in the wall of the crankshaft, where the space between is filled by hard soldering. What is important is to have the crankshaft 801 properly balanced at the end of the production process.

11G-W (abbreviated as "ESVT") relate to a motor having at least one elongated cylinder and a piston in communication with a crankshaft, according to Enclosed Space Volume Technology.

Figures 11G and 11H show the basic ESVT in two variants for the pressurization of a storage pressure vessel where the pump controlling the volume of the enclosed space is driven by a bidirectional actuator.
It is clear that different power lines are shown that separate the use of the power produced by the auxiliary power source.

FIG. 11G shows the configuration of FIG. 11A adapted for ESV-Technology, with a U-shaped axle 801'
The shaft 801′ includes two counterweights 804, a piston rod 805, and an expandable actuator piston 806. One end of the shaft 801′ may be connected to an electric start motor 830 that can obtain its energy from an accumulator 832, the aforementioned being powered by a solar cell 833, and/or
or other preferably sustainable (or optionally non-sustainable) power source (see Figures 15A-15F). At the other end, shaft 801' may be connected to a flywheel 835 (not shown), a clutch 836 (not shown), and optionally a gearbox 837 (not shown).

Inside the U-shaped shaft 801' there is a channel 1050 that is always in communication with:
The ESVT pump 1055 comprises a piston 1061 (eg, shown according to FIGS. 50-52 (inclusive)) and a conical chamber 1062 that regulates excess pressure relative to the total pressure within the channel 1050. The overpressure is controlling the speed of the motor. The motion of ESVT pump 1055 is 2
It is generated by a two-way actuator 1053 controlled by two reducing valves 1057 and 1058, respectively, each regulating the pressure on one side of a piston (not shown) within said two-way regulator 1053. Reduction valve 1057 is connected to two-way actuator 1053 by channel 3300
Reduction valve 1058 communicates with one side of the two-way actuator 1053 by channel 3301.
communicates with the other side of the Said pressure reducing valves 1057 and 1058 are preferably electrically interconnected (and optionally other solutions exist, but not shown) such that an increase in pressure on one side (on the side of said piston) Simultaneously reduce the pressure (on the side of the piston) to the motor and vice versa. Reduction valve 1057 is controlled by speeder 841 via controller 840'. The pressure reducing valves 1057 and 1058 communicate with the pressure storage container 890 via the feeder line [829]. The pressure reservoir 890 may be pressurized with fluid 1063 when the motor is generated.

The channel 1050 is also in constant communication with the piston rod 805 of the ESVT pump 1056. For details of the assembly of the connecting rod with the shaft 801', please refer to FIG. 11T. Accordingly, a change in volume/pressure of the ESVT pump may motor a change in volume/pressure within the actuator piston 806, and thus may motor the movement of the actuator piston 806.

The ESVT pump 1056 comprises a piston 1059 (shown, for example, according to Figures 50-52 (inclusive)), a conical chamber 1060 driven by a two-way actuator 1072, which adjusts the pressure of the channel by changing the volume of the channel, so that the actuator piston 806 changes the volume at a certain longitudinal position, according to Figures 10A-10F. The two-way actuator 1072 is driven by the reduction valves 1051 and 1052, similar to the ESVT pump 1055, by the two-way actuator 1053. However, the reduction valve 1051 is controlled by a sensor 1064, which transmits the rotational position of the shaft 801 to the reduction valve 1051 [1054], so that the piston 806 can be extended or retracted at the appropriate time depending on the pressure change. The reduction valves 1051 and 1052 can be in communication with a pressure source, for example the pressure storage vessel 890 [829]. The other side of the sealed space may be in constant communication with the sealed space 813 of the piston 806. The pressure reducing valve and associated equipment are in electrical communication with the battery 832 via wires [1069].

FIG. 11H shows the configuration of FIG. 11G (with the referenced components of FIG. 11G) with the addition of a pump 826 for recompression of the pressure storage vessel 890. The recompression cascade is identical to that shown in FIG. , at the appropriate time, provides a low pressure in the third enclosed space to allow depressurization of the actuator piston 806, but is not necessary for the ESV technology currently in use. The outlet [1070] of the two-way actuator 1072 is in communication with the pump 820, but can be connected to the power supply line [825] of the piston pump 826 if the pump 820 is not present. Required check valves are not shown. This (“consumption”) of 2-way actuators 1053 and 1072
In the configuration, the spaces on either side of the piston within the two-way actuator chamber are in direct communication with the communicating pump 826.

Pressure reservoir 890, and pressure reducing valves 1051, 1052, 1057, and 1058, respectively, which are
They communicate with the inlets of the two-way actuators 1053 and 1072, respectively, and with the spaces on either side of the piston (see FIG. 11 for a schematic diagram inside the two-way actuator 1053'). Necessary check valves are not shown. The reduction valves 1057-1058 and 1051-1052, respectively, are related to each other such that if one valve is opened more, the other valve is closed more at the same time. The valve means 840' of the reduction valve 1057 is actuated by a speeder 841, while the reduction valve 1051 is actuated by a sensor 1064 with communication [1054]. The reduction valves are electrically actuated through wires [1069].

The alternator 850 is in communication with the main shaft 852 and charges the battery 832 via connection [842]. Other auxiliary power configurations 851 are shown in Figs. 15A, 15B, 15C, 15E or 15F. The pump 826 may also be in communication with a flywheel (not shown) and/or a regenerative destruction system (not shown). As shown in Figs. 15A, 15B, 15C, 15E, 15F, other auxiliary power sources may be used, optionally non-sustainable sources of power.

11I-11N (inclusive) respectively show one (FIGS. 11I, 11K, 11M) and two cylinder motors (FIGS. 11J, 11L, 11N) partially machined with respect to the main components (e.g., axles and e.g., wheels and belts/gears) in communication with each other. The ESVT pump controlling the volume of the closed space is driven by a two-way actuator (FIGS. 11I, 11J), a crankshaft (FIGS. 11K, 11L), and a camshaft (FIGS. 11M, 11N) according to the configuration shown in FIG. 11H. The conical cylinder can have a different size for each power type, since the loops of the power types are different in size. The auxiliary power sources are referred to only by reference numbers. As shown in FIG. 15A, FIG. 15B, FIG. 15C, FIG. 15E, FIG. 15F, other auxiliary power sources can also be used, and optionally non-sustainable power sources can also be used.

Each drawing containing two cylinder motors consists of a "left" and a "right" enlarged view.
Figures 11I-11R show several configurations of one cylinder and two cylinder motors. One of the purposes is to show a clear update of the power supplied and the power used, which is also disclosed diagrammatically in Figure 15. Another purpose is to highlight the differences:

Controlling the pressure rebuilding of the actuator piston by a wire in communication with the distributed power, either a camshaft or a crankshaft. To increase the efficiency of the power delivered, Figures 11o-11R show a small Combustion motor shown. Several configurations of this combustion motor are shown. Another purpose is to show how the means for controlling pressure per cylinder may be combined or not included in a multiple cylinder motor. This objective indicated that it was first necessary to find out how the following cylinders interact with each other under the conditions of the combined crankshaft. In Figure 17A, BH (same figure), the power stroke of one of the two cylinders of the same motor is occurring simultaneously with the return stroke (series power) of the other cylinder; sea bream. 18A-G (Including) The power strokes of two cylinders of the same motor are working simultaneously (parallel power). It is then concluded which pressure control means (eg ESTV pump) and power lines (eg camshaft, crankshaft) may be combined for the two cylinders.

FIG. 11I is primarily based on the concept shown in FIG. 11H, using a two-way actuator 1072 to drive the ESVT pump 1056 to control the size of the enclosed space 1050+813. A partially assembled one piston-chamber combination 800' motor is shown that functions as shown in FIG. An actuator 1055 (piston 1061, chamber 1062) controls the speed of the motor. All observations regarding the presence of pump 820 made in the description of FIG. 11H are also valid here.

Only new issues are addressed here.
For details of the assembly of the actuator 1055 to the actuator 852, see FIG. 11S. The upper portion 1130 of the chamber 1062 of the actuator 1055 is attached to 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. 11S.

The actuator 1053' that changes the speed of the motor is the actuator 1053
, 1072 have different functions and therefore operate in a slightly different manner to the actuator 1053 shown in Figure 11H. In the configuration shown in this drawing of actuator 1053', spaces 1075 and 1076 on either side of piston 1078 within said chamber 1079 respectively communicate with each other via a number of check valves (not shown), see figure.

16A-C (inclusive) Thus, there is no return flow from said spaces 1075 and 1076 via pump 826 to pressure storage vessel 890. This may result in a loss of energy.
The spaces 1075 and 1076 communicate with the reduction valves 1058 and 1057, respectively. The chambers additionally communicate with each other via valve actuator arrangements 1121 and 1122, respectively, shown in FIG. 304, which may additionally be controlled according to HE or 211F of FIG. 2, if necessary. The valve actuator arrangements 1121 and 1122 are arranged opposite each other. The chamber 1079 of the actuator 1053' is attached to the motor main frame 5000. Details are shown in FIG. 16A-B.
The ESVT pump 1056 includes a chamber 1060 and a piston 1059 and is attached to the shaft 852. See FIG. 11U for suspension details. The two-way actuators 1053 and 1072 are driven by compressed fluid 1063 stored in a pressure storage vessel 890. The pressure reducing valve 1051 is actuated by a communication line [1054] and a power line [1069] via an electrical regulator 1065.

Pump 826 of FIG. 11H is described in detail in FIG. 11V. It receives its energy from an electric motor 830' which receives electricity via telecommunications [1080] from a battery 832. The circular motion of the shaft of the motor 830' is converted into translation and partial rotation by a kind of crankshaft 1217. If pump 820 is not present, flow from two-way actuator 1072 will be communicated to said pump 826 by channel [1083]. Compressed fluid passes from the pump 826 through the channel [828] to the pressure reservoir 890. Alternator 850 communicates with main shaft 852 via toothed belt 1073 and wheels 1074, 1077. It sends power to battery 832 via telecommunications 842. Electric drive system 830 is similar to the element in FIG. 11A.

Figure 11J shows an overview of the two cylinder motors, with details shown in the enlarged view. 11J left, 11J right.
FIG. 11J shows a partially fabricated two cylinder motor based on the concept shown in FIG. 11I. Details on combining two crankshafts, having the advantages of one component and performing similar tasks on several. In a two-cylinder motor, the last mentioned is not much, as it shows an example where the two actuator pistons are not in the same longitudinal position at the same moment (asynchronous crankshaft design), according to FIG. 17B. Each "cylinder", better referred to as a "chamber", is an enclosed space contained within its crankshaft (hereinafter "
1270 (FIG. 11X) between the channels of each sub-crankshaft.

Thus, each actuator piston has an ESVT pump that controls the volume of each enclosed space, and each ESVT pump is driven by a bidirectional actuator. Since the actuator pistons must (a) move synchronously, it may be necessary for the pressure reducing valves of each two-way actuator to be in communication with each other, eg electrically, for synchronization purposes. However, the pressure reducing valves may be communicated through the sub-crankshafts by sensors that measure the rotation of each sub-crankshaft 1064. Whether two ESVT pumps can be combined into one cannot be concluded without detailed consideration. See Figures 17C-17H (inclusive).

Therefore, there are two fast actuators and they must communicate with each other.
This can be done, for example, via the speeder 841-1 speeder that electrically controls both pressure reducing valves of each two-way actuator 1057. Whether two two-way actuators can be combined into one cannot be concluded without detailed study. See Figures 17C-17H (inclusive).

There are two or one pressure storage vessels, which are factory pressurized and recompressed during operation by the pump. One pump, which can be driven by electricity from a factory charged battery 832, can be recharged during operation by an alternator 850 in communication with the main motor shaft 852. This battery can also be charged by an external power source, for example via a cable. The pressure storage vessel 890 can be repressurized via a hose in communication with a pressure source, preferably a medium pressure canister or optionally a high pressure canister, or an external pump (for example most efficiently driven by a windmill). Auxiliary power sources are according to Fig. 15A, B, C, E, F, at least one of which can charge the battery.

First, if there are three or more four-cylinders in one motor, the inlet/outlet of the two-cylinder actuator for speed control can be combined with the inlet/outlet of the ESTV pump to reduce the total number of said two-cylinder actuators and pumps. See Figures 17C-17H (inclusive). Pump 820 may be redundant.

The two sub-crankshafts on the main motor shaft are connected to each other by a connector, details of which are shown in the figure. 11W, 11W, 11X are slightly reduced in the plane perpendicular to the central axis of the crankshaft to compensate for possible timing differences in the shape change of the actuator piston due to the elastic properties of the walls of the actuator piston during recompression. May be flexible.

The left side of Figure 11J shows a scale-up of the left part of Figure 11J.
Figure 11J right shows a scale-up of the right part of Figure 11J.
FIG. 11K shows a single cylinder motor based on the concept shown in FIG. 11H, using an auxiliary crankshaft instead of a two-way actuator to drive the ESVT pump. The auxiliary crankshaft is driven by an electric motor powered by the battery. The battery is recharged during operation by an alternator in communication with the main motor shaft. Since the speed of the speed actuator needs to be adjusted with the speed of said ESVT pump, the speedometer 841
, the pressure reducing valve 1057, and the electric motor 3500 are in communication.

They are connected to each other by a wire [3501] via an electrical/electronic regulator 3502. A motor 3500, also shown in the following FIGS. 11L, 11M, and 11N, drives a crankshaft 3503 via, for example, a toothed belt 3505 and wheels 3506, 3507 that drive an ESVT pump 1056. The electric motor 3500 is connected to the battery 832 by a wire [3504] via the regulator 3502.

The (auxiliary) crankshaft is used to drive an ESVT pump mounted on a fixed crankshaft axis, with a connecting rod connecting the piston rod of the ESVT pump to the crankshaft (see Figure 11C for the actuator piston). or the connecting rod is missing, and the pump vibration structure shown in FIG. It rotates around the crankshaft. Assembly of the ESVT pump on the main shaft is similar to if the pump were not vibrating (see, eg, FIG. 11U), but the fit of the bottom of the pump to the shaft may be slightly larger.

The two-way actuator 1072 of the ESVT pump has been replaced by an auxiliary crankshaft, and the two-way actuator 1053 has been replaced by the pump 826 due to the fact that the pressure storage vessel does not need to be repressurized, rather than remaining pressurized. can be smaller than that shown in FIG. 11I. This is the preferred solution, and a solution where pump 820 was redundant while having pump 820 is an optional solution.

Figure 11L shows an overview of the two cylinder motors, with details shown in the scaled-up view. 11L left, 11L right.
Figure 11L shows a two cylinder motor based on the concept shown in Figure 11K, each cylinder has a closed space, so the ESVT pump controls the volume of each cylinder, and both are driven by the same auxiliary crank. Driven by a shaft axis.

Since the speed of the speed actuator needs to be coordinated with the speed of said ESVT pump, if both ESVT pumps use the same axle with both crankshafts, the speed 841/reducing valve 1057 and the electric motor Both controls of the 3500 are in communication with each other.

Since the ESVT pump's two-way actuator 1072 has been replaced by an auxiliary crankshaft, it can be made as one piece due to the fact that the assembly with the connecting rod and crankshaft is simple (no channel) and the fact that the two-way actuator 1053 does not require repressurization rather than maintaining pressurization of the pressure storage vessel. Because of this, the pump 826 may be smaller than the one shown in FIG. 11I, although it may require limited repressurization. This is the preferred solution for two cylinder motors, while a solution with pump 826 may be used in cases where pump 820 is not an option.

The left side of FIG. 11L shows a scale-up of the left portion of FIG. 11L.
FIG. 11L right is an enlarged view of the right side of FIG. 11L.
FIG. 11M illustrates a one cylinder motor based on the concept shown in FIG. 11H, using a camshaft to drive the ESVT pump instead of a two-way actuator.

The camshaft is driven by an electric motor powered by the battery. The battery is recharged during operation by an alternator in communication with the main motor shaft. Since the speed of the speed actuator needs to be coordinated with the speed of the ESVT pump, the speedometer 841, pressure reducing valve 1057, and both controls of the electric motor 3500 are in communication with each other as shown in Figure 11K. ing.

The camshaft 3515 has a limited height of the cam 3516 to lift the piston rod of the ESVT pump 1056, which means that the stroke length of the ESVT pump will be shorter than that of Figures 11K and 11L and the auxiliary chamber will be wider to obtain the required volume change. In addition, a spring may be required to reverse the piston movement initiated by the cam.

The ESVT pump's two-way actuator 1072 has been replaced by an auxiliary camshaft, and the two-way actuator 1053 now operates by rotating the pressure reservoir instead of keeping it pressurized.
Due to the fact that there is no need to repressurize, pump 826 may be smaller than that shown in Figure 11I. This is the preferred solution, while a solution having pump 820 while pump 826 was redundant is an optional solution.

Figure 11N shows an overview of the two cylinder motors, the details of which are shown in enlarged views: 11N left, 11N right.
FIG. 11N shows a two cylinder motor based on the concept shown in FIG. 11M, where each cylinder has an enclosed space and the pump therefore controls its volume, and both are driven by the same camshaft.

Since the speed of the speed actuator needs to be coordinated with the speed of said ESVT pump, if both ESVT pumps use the same camshaft axis, the speed 841/pressure reducing valve 1057 and the electric motor 3500 will be controlled by the electronic/electrical regulator 3502. They communicate with each other by wires [3501].

Due to the fact that the ESVT pump's two-way actuator 1072 has been replaced by a camshaft and the two-way actuator 1053 does not need to re-pressurize the pressure reservoir rather than keeping it pressurized, pump 826 may be smaller than that shown in FIG. 11I. This is the preferred solution for a two cylinder motor, while a solution with pump 826 may be used in cases where pump 820 is not an option.

The left side of FIG. 11N shows a scaled up version of the left portion of FIG. 11N.
Figure 11N right is an enlarged view of the right-hand portion of Figure 11N.
11O,P,11Q,R (inclusive) relate to the configurations of Fig. 11K,L (crankshaft) and Fig. 11K,L (crankshaft), respectively. The auxiliary power source is a configuration according to Fig. 15C, in addition to the solar cell 833, in which a combustion motor 3525, preferably using H2 (and any other combustible power source), preferably produced by electrolysis from conductive H2O (and from a canister, whether pressure-cooled and liquefied or not), is in direct communication with the ESVT pump controlling the volume of the enclosed space. Instead of the configuration of Fig. 15C, different configurations can be used, such as the configuration of Fig. 15D. The fact that the combustion motor directly drives the power line (ESVT pump), the crankshaft/camshaft, rather than the first generated power driving the electric motor,
This means that it has about four times the efficiency. Each figure shows a different type of cooling for the combustion motor. The fluid (e.g., air) heated by the combustion motor may be used for heating purposes, for example to heat a compartment of a vehicle.

Figure 11O shows a one cylinder motor using a crankshaft to drive an ESVT pump based on the concept described above. Here we only address the new issues.
For the motor to operate properly, several components within the motor must be synchronized.

A certain amount of H2 and O2 is used by the combustion motor through electrolysis of H2O to drive the crankshaft and drive the ESVT pump,
The communication between the ESVT pump and the two-way actuator for the velocity actuator is covered in the descriptions of Figures 11K, 11L, 11M, and 11N.

The motor also drives a pump 826, shown in FIG. 11V, via a toothed belt and wheels for recompressing the pressure storage vessel 890.
The configuration of the auxiliary H2-burning motor (according to FIG. 15C) comprises a storage tank 1612 for conductive H2O 1613 (which may be H2O from a tap, or a conductor, e.g. salt, or simply seawater), a filler opening 1614, and an outlet channel [1615] to a container 1616, where the electrolysis 1617 of said water 1613 is taking place. A wire [3547] connects the speedo 841 with a regulator 3509, controlling the level of H2 and O2 production by electrolysis. No check valves are shown. A power line [3547] from the battery 832 to the container where the electrolysis is taking place. The hydrogen obtained is transported [3545] to said motor by a pump, but the very necessary check valve is not shown. The resulting O2 is also transported [3546] to said motor by a channel + pump - the very necessary check valve is not shown - which is used as a kind of turbo. The H2 motor 3525 is shown in this figure as being air cooled, where warm air is transported through channels [3538] directly or indirectly by a liquid to a heat exchanger 3539, for example for the purpose of warming up the cabin of the vehicle (arrow 3540).

Figure 11P shows an overview of the two cylinder motors, with details shown in the enlarged view. 11P left, 11P right.
Figure 11P shows a two cylinder motor based on the concept shown in Figure 11O, each cylinder has an enclosed space, so the ESVT pump is both driven by the same crankshaft, and the two high speed actuators , one auxiliary motor. The crankshaft is H2O
is driven directly through the gear wheel 3526 by a liquid cooled combustion motor using H2 derived by electrolysis. The crankshaft drives the pump 826 which drives the ESVT pump and recompresses the pressure storage vessel 890. The illustrated toothed belt 3527 may be replaced by gears.

There is a water pump 3528 for circulating cooling water 3529 from an air-cooled radiator 3530 to another radiator 3531, which can warm air from the surroundings, for example to warm the cabin of a car. The water pump is in communication with the motor main shaft 852 and an alternator 850 that recharges the battery 832.

The left side of Figure 11P shows a scale-up of the left part of Figure 11P.
Figure 11P right shows a scale-up of the right part of Figure 11P.
FIG. 11Q is a diagram illustrating a single cylinder motor with a camshaft to drive an ESVT pump based on the above concept. The principle of the camshaft in Figure 11Q is the same as that in Figure 11M. The camshaft is driven directly by auxiliary power from a forced gas (eg, air) cooled combustion motor. The pump that recompresses the pressure storage vessel is driven directly by the combustion motor. The battery 832 is being charged by an alternator attached to the main motor shaft or according to Figure 15.D.

Figure HR shows a schematic of a two cylinder motor, the details are shown in the scaled up figures. 11R Left, 11R Right Figure 11R shows a two cylinder motor based on the concept shown in Figure 11Q, each cylinder has an enclosed space, each cylinder has an ESVT pump that controls the volume driven by the same camshaft. The whole concept is known from the previous drawings.

The left side of Figure 11R shows a scale-up of the left part of Figure 11R.
FIG. 11R shows an enlarged view of the right portion of FIG. 11R.
Figures 11S-W (inclusive) show details of some of the components used in the figures. 11A-R (including)
FIG. 11S shows details of the joint of the piston-chamber combination pump 1061 with the main shaft 852 of the motor according to FIGS. 11I-11R using ESV technology. The base pump 1140 comprises two base parts 1141 and 1142, which are bolted together around the main shaft 852 with a suitable fine fit by two bolts 1143 and washers 1144. The base part 1141 is bolted to a motor housing 1145 that has a bearing 1146 around the rotating main shaft 852. The motor housing is shown as hatch 5000. The base 1141, 1142 has an O-ring 1148 that seals the sliding connection between the main shaft 852 and the base 1141, 1142. Pump chamber 1149 communicates with third sealed space 1150. Bolt 1151 and washer 1152.

Figure 11T shows a detail of the joint between the connecting rod 805' of the actuator piston 806 and the crankshaft 801' on the motor shaft 852 according to Figures 11G-11R, using continuous communication between the enclosed space 813 of the actuator piston 806 and the channel 1050 of the crankshaft 801' using ESV technology.

Assembly of the connecting rod 805' and the U-bend shaft 801' is shown at one point in Figures 11G-11R. The connecting rod 805' and the U-bend shaft 801' rotate relative to each other. The U-bend shaft 801' is assembled with the connecting rod 805' bearings 1100, 1100" and O-rings 1104, 1104"' between the connecting rod 805' and the shaft 801'. The sealed space 813 communicates with the channel 1050 through holes 1106, 1107 and 1108. To avoid stresses in the axle 801', there are several holes on the circumference of said axle 801' at different circular locations at a distance from each other. The channel 1050 is connected to the open spaces 1105 and 1105'.
Through these, the holes 1106, 1107, and 1108 are constantly in communication with the sealed space 813.
There is constant 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 parts 927' and 928', and the central axis 929 of the channel 1050 is at a parting surface (not shown) of the base 926'. Two bolts 1110 and a ring 1111 on either side of the piston rod 805' hold the two parts 927', 928' together.

FIG. 11U shows details of the joint of the piston-chamber combination pump 1060 with the main shaft 852 of the motor according to FIGS. 11I-11R using ESV technology. The base 1180 of the pump 1060 is 2
It has two bases 1181 and 1182, which have two bolts 1183 and washers 1184.
are bolted together around the main axis with a suitable micro-fit. The base portion 1181 is bolted to a motor housing 1185 having a bearing 1186 around the rotating main shaft 852. The motor housing is shown as hatch 5000. Bases 1181 and 1182 have an O-ring 1188 that seals the sliding connection between main shaft 852 and bases 1181 and 1182. Pump chamber 1189 communicates with second sealed space 1190. Bolt 1191 and washer 1192.

FIG. 11V shows the mechanism driving the pump, eg, 826, of FIGS. 11H-11R, and its base.
Pump 1200 includes a chamber 1201, a wall 1206, a base 1202, and a top 1203 of chamber 1201. Piston 1204 is of the type described in section 19640 of this patent application and is a pressure measurement sensor 1205 at the end of piston rod 1214. The bearing 1207 of the upper part 1203 of the pump 1200 is preferably made in accordance with section 19597 of this patent application. This means that bearing 1207 can withstand large lateral forces from piston rod 1214. The base 1202 of the pump 1200 can rotate about an axis 1208 within the boundaries 1222 of another base 1209 that is part of the motor housing 1210, shown as a hatch 1211. On the base 1202, on the opposite side of the shaft 1208 from the chamber 1201, there is a contraweight 1212 assembled to balance the pump 1200 in a center point 1213 of the shaft 1208. The pump 1200 comprises a piston rod 1214, which is guided by the bearing 1207 of the upper part 1203 of the pump 1200. One end of the piston rod 1214 has an assembled piston 1204, while the other end of the piston rod 1214 has an assembled shaft 1216. The shaft 1216 is disposed perpendicular to the piston rod 1214, and the piston rod 1214 is attached to the shaft 1216. The disk 1217 includes an axis 1218, the axis 1216 being rotatable and preferably centrally located on the disk 1217 near a side 1219 of the disk 1217. The disk 1217 rotates around a disk shaft 1220 that communicates with an electric motor 1221. Rotation of the axis 1220 causes the disk 1217 to rotate by causing the axis 1216 to rotate about the axis 1220 and centered in a plane perpendicular to the disk 1217. this is,
While the piston rod 1214 rotates the chamber 1201 of the pump 1200 from one boundary 1222 to the other boundary and vice versa within angles s and t with respect to the central axis 1223 of the pump 1200, This means that there is a translational movement to and from the top 1203 of the pump 1200. This causes piston 1204 to move within chamber 1201. The inlet 1224 (not shown) and the outlet 1225 (not shown) of the pump 1200 are part of the base 1202 of the pump 1200 by using the type of piston 1215, and the inlet 1224 and the outlet 1225 may include a check valve. Media 1226 of said pump 1200. If another type of piston is used, the locations of inlet 1224 and outlet 1225 may differ from those described above.

FIG. 11W is a diagram showing a connection joint between the crankshafts of the two cylinder motors in FIGS. 11J, 11L, 11N, 11P, and 11R. The illustrated connecting joint is an improvement of the version shown in the figures of the drawings. 11J, 11L, 11N, 11P, 11R In this figure a version of this connection joint is shown, in which adjacent enclosed spaces communicate with each other. The crankshaft 1250 on the left side of the cylinder (not shown) includes a channel 1251 that functions as a (second) enclosed space. An end 1253 of the crankshaft 1251 faces an end 1254 of the crankshaft 1252 on the right side of the cylinder (not shown), and between the ends 1253 and 1254 a gasket 1255 is provided within flanges 1256 and 1257. located compressed in the direction (“embedded”). Consists of both crankshaft ends 1253 and 1254. The last mentioned crankshaft 1252 is provided with a channel 1265 that serves as a (third) enclosed space and communicates with the right cylinder (not shown). Each flange 1256 and 1257 preferably has an uneven number of holes, with holes 1258 shown. Within the hole is a thin flexible cylinder 1259 mounted in close contact with the hole 1258. The cylinder 1259 has a bolt 1260 positioned with a path fit. This thin flexible cylinder 1259 allows for very small differences in the angular positions of the two assembled crankshafts 1250 and 1252 that can result from asynchrony due to the asynchronous movement of the actuator pistons (not shown). . Washer 1261 and nut 1262.

FIG. 11W shows the improved seal of gasket 1263 (with respect to gasket 1255).
Flange 1256 has a cavity 1264 and flange 1257 has a hump 1265 (not shown) that fits into cavity 1264. If flange 1257 were flat, the connection would be flexible, but a clamping alternative is shown.

FIG. 11X shows the same as FIG. 11W, except that the clamping rods 1270 are arranged in channels 1271 and 1272, among which the common channel parts 1273 and 1274 are arranged in turn, so that communication between the channels is not possible. Each has a larger diameter to obtain shoulders 1275 and 1276. The degree of clamping of said clamping rods 1270 in one of the channels 1273 or 1274 is obtained, for example, by applying a suitable fit and soldering to one of the ends. Improved sealing of the gasket 1263 - this structure is identical to that shown in FIG. 11W.

Instead of a toothed belt on the power side of the motor according to Fig. 11D-W, where the pump is driven, it is very often replaced by a gear.
Figure 12A shows the motor configuration 800 of Figure 11B, where the piston-chamber combination was in communication with the main shaft via the crankshaft, but in this figure with a fixed chamber with a piston rotating clockwise according to Figure 10A or Figure 12B, the suspension of this piston is replaced by a configuration 800' shown in Figure 12C. A "black box" is shown for the inlet, which communicates with a speed reducer valve 840 via a channel [.............], and for the outlet, which communicates with a pump 818 via a channel [817]. The speed reducer valve 840 is controlled by a speeder 841.

FIG. 12B shows a motor in which the piston of the actuator piston-chamber combination is moving, but the chamber is not moving. The motor with a chamber 960 comprises four sub-chambers 961, 962, 963 and 964, each located in succession to one another around the same central axis 965, with an axis 966 through the center 967 of the chamber 960. Inside said sub-chambers 961, 962, 963 and 964, one piston 968 is arranged, respectively, in two critical positions, namely 968 in the first rotational position of the sub-chamber 964 having the largest diameter; ' position and 968'' position when in a second rotational position of subchamber 961 lying in series with subchamber 964, resulting in a first rotational position of subchamber 964. The position is closest to the second rotational position of the secondary chamber 961 having the smallest diameter. Four holes 967 are shown for assembly.

FIG. 12C (consumption) shows the AA section of FIG. 12B, with a non-movable chamber 960 and movable pistons 968′ and 968″. The sealed space 1070 of the pistons 968′, 968″ (the same pistons of two different sizes) ends at the axis 966, where two pistons arranged on either side of the sealed space 1070
The sealed space 1070 communicates with a second sealed space 1072 in the shaft 966, where a T-valve 1074' is present and ends in a housing 1073 controlling the inflow of fluid 822 from the pressure storage vessel 814 through a flow passage [829] and a return valve 840. Said fluid 822 controls the pressure in the pistons 968' and 968". The outlet from said pistons 968', 968" goes through a channel [817] to the cascade of pumps (translational or rotational).

Electrical signal 1076 is in communication with electrical/electronic control unit 1077 which controls T-valve 1074' within housing 1073 via signal [1078]. Rotation of shaft 966 thereby controls the pressure within said T-valve 1074' and thus piston 968', 968''. Signal [891] from pressure source 1075 to control unit 1077. Flange 1079 controls pressure within chamber 960. is connected to a suspension 1080 attached to shaft 966. Belt 1081. Pumps may be present, such as, for example, references 821' and/or 826' in Figure 13B, but not yet shown in this figure. ie, the pump is in communication with a pressure source 1075. The pump may be in communication with shaft 966 and may also be in communication with a flywheel and/or regenerative fracture system 1082.

FIG. 12D (closed space) shows section AA of FIG. 12B, with a non-movable chamber.
960, pistons 968' and 968" can be made movable. The pistons 968', 968"
The sealed space 1070 ends at the shaft 966, where it is sealed with two O-rings.
communicates with a second sealed space 1072 within shaft 966 and terminates within a housing 1073, where there is a piston-chamber combination 1074 which controls the pressure within pistons 968', 968".
(The same piston in two different sizes.) The piston-chamber combination may be connected to fluid 889 of a power source 1075 via channel 890.

The electrical signal [1076] is in communication with an electrical/electronic control unit 1077, which controls a piston-chamber combination 1074 in a housing 1073 via a signal [1078]. Rotation of the shaft 966 thereby controls said piston-chamber combination 1074 and thus the pressure in the pistons 968', 968". A signal [891] from the pressure source 1075 to the control unit 1077. The return channel 1050 with the reduced pressure fluid (in said fluid 889) returns to the power source 1075 via a cascade recompression system (translational and/or rotary pumps) (see FIG. 12A). 1151.
A flange 1079 connects the chamber 960 to a suspension 1080 attached to the shaft 966. A belt 1081. A pump may be present, for example as reference 82 P and/or 826' in FIG. 13B, but is not yet shown in this figure. That is, said pump communicates with a pressure source 1075. Said pump may be in communication with the shaft 966. It may also communicate with a flywheel and/or a regenerative destruction system 1082.

The motor according to Figures 12A and 12B may include a chamber 960, at least a portion of which may be parallel to the central axis of said chamber (not shown).
FIG. 13A shows the motor shown in FIG. 11A, where the crankshaft arrangement 800 has been replaced by the rotary motor of FIG. 10B.

FIG. 13B shows the motor of FIG. 13A in which the piston pumps 818 and 826 have been replaced by rotary pumps, for example centrifugal pumps 821' and 826'.
FIG. 13(C) is a cross-sectional view taken along line BB of FIG. 13(B), in which 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 with chamber 860 comprises four sub-chambers 861, 862, 863 and 864, each located successively around the same central axis 865, having an axis 866 passing through the center 866 of chamber 860. Five pistons 868, 869, 870, 871 and 872 are arranged within said sub-chambers 861, 862, 863 and 864, respectively, each piston 861, 862, 863 and 864 being arranged at a different rotational position from the other, at an angle a = 72°.
Piston rods 873, 874, 875, 876, and 877. Pistons 868, 869, 870, 871,
and 872 are shown to be "ball" shaped and all have different diameters. The chamber 860 rotates counterclockwise around the axis 866 and sub-chambers 861, 862, 863, and 864 having a first rotational position and a second rotational position in a clockwise rotational direction, and four holes 878 are shown for assembling the chamber 860 to the axis 866.

Fig. 13D shows a cross section AA of Fig. 13C. A chamber 860 having a cutout 879 around the flange 861 of said chamber 860 can be fitted with a belt 883. The chamber 860 is assembled to said shaft 866 having a flange 880 by a setback. The piston rods 873, 874, 875, 876 and 877 are assembled inside a housing 882.

Figure 13E shows section CC of Figure 13A and another section of said housing 882 in view AA. Piston rods 872, 873, 874, 875, 876 are connected to a pressure distribution center 884, each piston is connected to a steering pressure reducing valve system 886, which provides the necessary pressure to each piston rod, and a signal 887 that gives the computer 885 the rotational position of said axle 866, which determines the pressure of each piston by a signal 888. The pressure to said piston rods 872, 873, 874, 875, 876 passes through a channel 890 from the pressure.

The container 889 is controlled by signals 891 to a computer 885. The fluctuating pressure changes in the enclosed spaces of each piston are also processed electronically for each piston by the same computer 885, although both are processed separately. Pumps (such as references 821' and/or 826' in FIG. 13B) may be present, but are not yet shown in this figure. Said pumps communicate with a pressure source 1075. Said pumps may communicate with the shaft 966. They may also communicate with a flywheel and/or a regenerative destruction system.

FIG. 13F shows a schematic of an alternative solution for the motor recompression system, now similar to FIG. 11F. Each sealed space (e.g., 1090) of each piston communicates with a piston-chamber combination 873, 872, 874, 876, 875, while 873 communicates with the following actuator piston 1091.
including.

Its position in the chamber 1092 is controlled by the position of the cam wheel 1093, which can reverse the cam 1094 while the cam 1093 is assembled on the shaft 866. NB: The cam and the wheel are shown diagrammatically because each wheel has a different distance to the associated piston and the wheels are required to be shown (partially) in sideways. The pressure in the enclosed space 1090 can be regulated by another piston-chamber combination 1055', which is an analogue 1055 of FIG. 11F, another control actuator 1056' (as 1056), and reduction valves 1057', 1058' (as 1057, 1058), while adding a speeder 841' (as 841). A pressure vessel 889 communicates with said reduction valves 1057' and 1058' [1095]. Pumps (such as, for example, references 821' and/or 826' of FIG. 13B) may be present, but are not yet shown in this figure. The pump is in communication with a pressure source 1075. The pump may be in communication with a shaft 966. It may also be in communication with a flywheel and/or a regenerative destruction system.

The motor according to Figures 13A, 13B, and 13C can include a chamber 860, at least a portion of which can be parallel to the central axis of the chamber (not shown).
FIG. 14A shows the central shaft 1702 and piston 1703 mounted on a piston rod 1704 as it moves from a second longitudinal/second circular position 1705 to a first longitudinal/first circular position 1706. 17 shows changes in pressure and size of an actuator piston 1700 disposed within a chamber 1701 having a The actuator piston 1700 is pressurized to, for example, a 31/2 bar in said second longitudinal/second circular position 1705. The piston 1700 includes a sealed space 1707 containing a pump section 1708. The pump portion 1708 of the enclosed space 1707, separated from the rest of the enclosed space 1707 by the piston 1703, e.g. actuator piston in said first longitudinal/first circular position when pressurized to said 31/2 bar at second longitudinal/second circular position 1705 until depressurized to /2 bar; 1709 has a much larger diameter than said piston 1705 in said second longitudinal/second circular position. In order to retract the actuator piston 1705 to atmospheric pressure (position 1713), in the case of the crankshaft, a -1/2 bar overpressure returns towards the second longitudinal position, causing the piston 1703 to retract to the actuator piston 1709. The closed space 1707 is released by pulling it away from the closed space 1707. The diameter of the actuator piston 1711 is greater than the diameter of the actuator piston 1700, which was pressurized to 31/2 bar at the second longitudinal position 1705 within the chamber wall (not shown in this view). Slightly smaller, its production size has increased. Said piston 1703 is retracted further away from said actuator piston 1711, resulting in a pump stroke 1716 towards a second longitudinal position 1714, and in the case of a crankshaft, the actuator piston moves towards a first longitudinal position. Upon returning to (1715), the actuator piston can be pressurized to 3 1/2 bar.

FIG. 14B shows the process of FIG. 14A in a time-schematic manner, with the sub-chambers 1720 arranged around a circular central axis 1721, which is additionally drawn as a straight line, which is a time line. The sub-chambers 1720 move normally in the direction of the arrow 1740, while the actuator piston 1722 does not move. However, in this figure, the sub-chambers do not move while the piston 1720 moves. The piston 1722 is arranged in a second longitudinal/circular position, and the fluid 1723 in the actuator piston is pressurized, for example to 3½ bar. The pump 1724 comprises a piston 1725, a piston rod 1726, a chamber 1727, and a cam wheel 1728. The cam wheel 1728 rests on a cam surface 1729. The piston 1725 is the second pump 1724.
The position of said piston 1725 remains unchanged as the actuator piston 1722 moves from the second longitudinal/circular position to the first longitudinal/circular position in said sub-chamber 1720, and the fluid 1723 reduces its pressure to the 1/2 bar actuator piston 1732. The cam wheel surface 1728 remains in position as the cam surface 1729 maintains its height. Retracting the piston 1725 from position (1730) to position (1731) provides the actuator piston 1733 with an internal pressure of 0 bar, reducing its diameter to its production size. This is a result of the cam wheel 1728 moving further away from said actuator piston 1733:cam wheel 1738, as the cam surface 1734 is inclined at an angle a to the cam surface 1729. Thereafter, immediately, the cam wheel 1738 at end point 1735
and back to said actuator piston 1733 towards actuator piston 1736. When cam wheel 1738 returns to its original surface 1729 it covers an inclined cam surface 1739 having an angle β (>90°) with said cam surface 1729. Actuator piston 1737 belongs to said position of said cam wheel 1728. It should be emphasized that the reduction in the diameter of the actuator piston may be done gradually over a very short period of time such that the actuator piston remains in contact with the wall 1748 of said chamber 1720.

Figure 14C shows the configuration of Figure 14B allowing injection of fluid into the actuator piston when the actuator piston is in a second circular position. The cam wheel 1740 then rotates across the hose 1741, creating a chamber 1744 with a wall 1742 and a fluid or mixture of fluids 1743. The hose 1741 has an outlet 1745 to the closed space 1746 of the actuator piston 1747 that is temporarily closed and open only to the closed space 1746 of the actuator piston 1747 when the actuator piston 1747 is in a second position (see Figure 14B) where the actuator piston 1747 may be recompressed from the fluid in the hose 1741.

The illustration of FIG. 14D1 shows a classical (linear cylinder) pump operating in the same circular chamber and communicating with the enclosed space of the actuator piston. The chamber 1749 has a central axis 1750 in a wheel 1751 rotating counterclockwise about an axle 1752 mounted with a roll bearing 1753. The chamber comprises four identical subchambers 1754, 1755, 1756, and 1757. Said channel 1750 includes five fixed and identical pistons 1758, 1759, 1760, 1761 and 1762, each in a different circular position relative to each other and thus having a different diameter and internal pressure. Each piston has a pump portion 1763, 1764, 1765, 1766, and 1767, which is fixed at the center of each of said pistons 1758, 1759, 1760, 1761, and 1762. Each of the pumps has a piston rod 1768, 1769, 1770, 1771, and 1772 with a cam wheel 1773, 1774, 1775, 1776, and 1777 running on a camshaft 1778. This camshaft 1778 is connected to the
with double identical descending portions 1779, 1780, 1781, and 1782. The actuator piston 1761 shows the use of a lowered part for the pump, with 1761' shown in dashed lines. arrow 1783
indicates the direction in which the chamber 1749 is pivoted about the axis 1752.

14D2 is the same as FIG. 14D1, except that pump parts 1763, 1764, 1765, 1766, and 1767 (including straight cylinders) have been replaced by pump parts 1786, 1787, 1788, 1789, and 1789 (including elongated conical cylinders). The second longitudinal positions of pump parts 1786, 1787, 1788, 1789, and 1790 are located closest to actuator pistons 1791, 1792, 1793, 1794, and 1795.

Fig. 14E shows part A-A of a motor according to Fig. 14D2 of the invention, with a circular chamber mounted directly on the wheel of a vehicle. A section of a rim 1900 with a central axis 1901 and its suspension on a brake disc 1902, with a central axis 1903 and brake pads 1904 mounted by bolts 1955 on a chamber housing 1905 in which a circular chamber 1906 is present, with a central axis 1907, said chamber 1906 is shown in a section with a spherical piston 1908 in a first circular position according to the configuration of Fig. 14D2. The inside of said piston 1908 communicates with an enclosed space 1909 mounted in a housing 1910, itself mounted by bolts 1922 on a part 1911 of a vehicle frame 1912 (not shown). The size of the enclosed space 1909 is adjusted by a pump 1913 having a conical chamber 1914, the end of which runs on a cam profile 1916 by a roller 1915. The cam profile 1916 is driven by an auxiliary electric motor 1917, which rotates the cam 1916, which rotates independently of the motor (including the circular chamber 1906 and the spherical piston 1908) by means of roller bearings 1924 around the main motor shaft 1918. The main motor shaft
A roller bearing 1919 for the chamber 1906 suspension on 1918 and a ball bearing 1920 for the cam profile 1916 on the main motor shaft 1918 are shown. The main motor shaft 1918 is also attached to the vehicle frame 1912 (not shown) by bolts 1923. A pressure controller 1925 ("drive by wire") according to the configuration of FIG. 16 communicates with a remotely positioned speeder 1927 (not shown). A pump 1928 of the pressure controller 1925 communicates with a channel 1926 that contains the enclosed space 1909 of the actuator piston 1908. An electric motor 1917 is shown diagrammatically as a rotor 1928 fixed to an outer motor wall 1929 that contains the cam 1926. An anchor 1930 is fixed to the main motor shaft 1918 such that the anchor 1930 is within the rotor 1928. The chamber housing 1905 is fixed to the main motor shaft 1918 by a nut 1931 and a washer 1932. The extended shaft ends 1933 of the rollers 1915 of the pump 1913 are guided.

Translation of the chamber 1914 of the pump 1913 is caused to occur within a groove parallel to the central axis 1934 of the pump 1913.
FIG. 14F shows a scaled-up detail of the section shown in FIG. 14E, said circular chamber 1916 in a first circular position with central axis 1907 and chamber housing 1905 bolted together by bolts 1955. show. A spherical piston 1908 is shown in section. The wall 1939 of said spherical piston 1908 is provided with a reinforcement (not shown) according to FIGS. 208E, F or FIGS. (eg, vulcanized) opposite the end 1941 closest to the pump 1913. The piston rod 1942 has a channel 1944 that communicates with the cavity 1946 of the spherical piston 1908 through a hole 1945. The other end 1941 of the wall 1939 of the spherical piston 1908 is the channel 1944 communicating with the conical chamber 1914 of the pump 1913 and communicating with the channel 1926 of a pressure controller (1925) (not shown). . The end 1941 includes a movable cab 1947 that is sealed to the piston rod 1942 by an O-ring 1948. A spherical piston 1908 is attached (eg, vulcanized) to the movable cab 1947, which can slide over the piston rod 1942. To make this drawing easier to understand, the wall 1941 of the piston 1908 is not drawn through the part where the contact between the wall 1941 of the piston 1908 and the wall 1948 of the circular chamber 1916 is made. central axis 1949 of channel 1944 of said piston rod 1942; central axis 1934 of chamber 1914 of said pump 1913; Said piston rod 1942 is movable within a cylinder 1950 and is sealed by two O-rings 1951 and 1952, respectively. a distance aa between the central axis 1953 of the hole 1945 and the central axis 1907 of the circular chamber 1916; The distance cc between the end 1954 of the movable cab 1947 and the central axis 1907.

If the vehicle has multiple wheels, it will be necessary to synchronize the movement of each wheel with the movement of each other wheel if the wheels are rolling on the same surface. This may be preferably done by a computer which coordinates the pressure in each actuator piston in each sub-chamber with the pressure in each of the other wheels. This is shown in Ref. 1960, where a computer (
(not shown) (1961).

FIG. 14G shows the same as FIG. 14H, except that the actuator piston 1908 is shown at a second circular post in the chamber 1916. The movable cab 1947 slides on the piston rod 1942 towards the closed end 1940, which slides (1925) in the cylinder 1950 towards a pressure controller (not shown). The hole 1945 is now located between the closed end 1940 and the movable cab 1947. The distance aa (FIG. 14F) has decreased to a distance bb, while the distance cc (FIG. 14F) has decreased to a distance dd. The sliding allows the position of the actuator piston 1908 to be adapted to be in the center of the cross section of the chamber 1916 in all circular positions of the actuator piston 1908.

FIG. 14H shows the configuration of FIG. 14E, where between the wheel rim 1900 and the brake plate 1902, the circular chamber housing 1916 was a built-in gearbox 1956, for example of the planet gear type.

In addition to computerized control of the pressure in each actuator piston, it may be necessary to synchronize the gear changes in the gearbox 1956 for each wheel, as described in FIG. 14E. This may again preferably be done by a computer, for example computer 1961, which already controls the pressure in each actuator piston (
Figure 14E).
Description of the Preferred Embodiment Updated from 19622 - FIG. 141 shows a part of a pressure management system of motors 1970, 1971. Each is mounted on at least two parallel arranged wheels. For example, in a car. The rear wheels 1974 and 1975 of said car are turning on their left edge about a center of a circle at 1976. The left wheel 1972 closest to said center 1976 is turning at a smaller radius 1977 than the right wheel 1973 having a radius 1978. The left wheel 1972 turns at an angle "a" and the right wheel turns at an angle "b", where "a">"b". Thus the left wheel turns slower than the right wheel and these signals 1981 and 1982 must be sent to the associated motors 1972 and 1973. This is because
The sensors 1979 and 1980 sense the different angles "a" and "b" as mentioned above. These signals are 1981 and 1982 which are forwarded to the computer 1983, which manipulates them and sends control signals 1984 and 1985 to the motors, thus causing the motors 1970 and 1971 to vary their respective speeds.

Figures 15A-E show several auxiliary power sources that work with the motor. The power lines shown have been carefully selected.
Figure 15A shows an H2 fuel cell sending electricity to the motor driving the ESVT pump. Today (February 2011), this solution is very expensive, but the Carbon Trust website has a message saying that there have been technological breakthroughs that make it possible to use H2 fuel cells in car motors in the future. Another problem is that hydrogen is difficult to store and is an unfriendly form of energy.

Figure 15B shows a solution to the H2 storage problem, as H2 is stored as H2O, freed by electrolysis. This method could generate H2 that could be used in a combustion motor to spin, as feasibility studies have shown that it requires less than 10% of the current energy required to run, for example, a car. The alternator is the generator that is driving the electric motor that drives the ESVT pump. The problem here is that the aforementioned process is only 25% efficient.

The O2 liberated by electrolysis of conductive H2O can be used in combustion motors, resulting in a more efficient combustion of H2 (turbo effect). The H2O generated from the combustion process in the combustion motor is
It can be reused to derive H2 by electrolysis.

Figure 15C shows a solution where the ESVT pump is directly driven by the shaft of the combustion motor via the crankshaft, which is more efficient since the process of powering the pump is 100% efficient. Can be made smaller.

Figure 15D shows a similar solution to Figure 15C, where the crankshaft is replaced by a rotating ESVT pump, making the process even more efficient. H2 now comes from both electrolysis and solar cells.

Figure 15E shows a solution where a large capacitor is used as its power source.
ESVT Pump This capacitor can be charged in a few minutes and has the great advantage that if the capacitor is the size of a suitcase, the car can be driven for 500km.

FIG. 15A schematically shows a storage tank 1630 of O2 (1631), which may be pressurized and is filled via a channel 1632 connecting the storage tank 1630 to the exterior (1633) of the motor. . The storage tank 1630 is in communication with the H2 fuel cell 1606 via channel [1634]. Another storage tank 1600 for H2 (1601) may be cooled and pressurized using electricity via telecommunications [1602] and via a channel 1603 connecting said storage tank 1600. Filled.

The storage tank 1600, external to the motor (1604), communicates via a channel [1605] to an H2 fuel cell 1606, where H2 and O2 are converted to electricity and charged via electrical communication [1607]. This charge is either a start battery 832B (short term, high current) or a service battery 832C (long term, medium current). The channel [1605] includes a non-return valve 1608 (not shown). The potential difference required for the operation of the fuel cell 1606 is established by the electrical communication [1602]. The start battery 832B is in electrical communication with the motor's starter 830 [1609] and the service battery 832C is in electrical communication with the motor's pump 820/826 [1610]. The motor, selected elements of which are rehearsed here, is treated in depth in Figs. 11A,B,G,H,I,J,K,L,M,N, and Figs. 12A, and 13A,B. The motor further comprises a pressure vessel 814/890 in communication with a pump 826 and a piston actuator device 800. The motor shaft 852 is in communication with an alternator 850, which charges via electrical communication [1611] a service battery 832A (long duration, medium current). The battery is in electrical communication [1602] with the cooling tank 1600. The batteries 832A-C (inclusive) are referred to as pieces and claimed as works in other figures of this patent application, reference number 832. A photovoltaic solar cell 833 additionally charges the battery 832. The pressure vessel 814/890 is charged by the pump 820/826. The motor piston actuator module 800 may alternatively be, for example,
Pressure reducing valve systems 1057 and 1058. FIG.

Figure 15B schematically depicts a tank 1612 of (conductive) H2O (1613). H2O (1613) is filled through a channel [1614] connecting the tank 1612 to the outside of the motor (1629). Said tank 1612 communicates via a channel [1615] to a container 1616 in which electrolysis 1617 of said water (1613) is carried out. The outlet [1622] of the container 1616 communicates with a combustion motor 1620 that communicates with its main shaft 1621. The channel [1622] includes a detent valve 1618 (not shown). The motor 1620 is combusting the H2 produced within the vessel 1616, thus creating motion. Here, it is the rotation of the axle 1621. The shaft 1621 communicates with an electric starting motor 1623 and an alternator 1624. The alternator 1624 is charged by the starting motor 1623's telecommunication line [1619] battery 832B (high current, short time) or battery 832C (medium current, long time). Battery 832A (moderate high current, long duration) is being charged by alternator 850 via electrical communication [1611] in communication with motor main shaft 852. The battery 832A is
Power is provided via telecommunications [1626] for electrolysis 1617 within vessel 1616. Battery 832C powers motor pump 820/826 via telecommunications [1627], and battery 832B powers starting motors 1623 and 830, respectively, via telecommunications [1628]. The above battery (832) is being charged during work. A photovoltaic solar cell 833 additionally charges a battery 832. Pressure storage vessels 814/890 are charged by pumps 820/826. Motor piston actuator module 800.

FIG. 15C schematically shows the process according to FIG. 15B, in which a piston pump 1625 of the recompression cascade is additionally connected to the combustion motor via a crankshaft 1636 and a piston rod 1637, either 820 or 826. It communicates directly with the main shaft 1621 of 1620. In addition to an alternator 850, a photovoltaic solar cell 833 that charges a battery 832 is in communication with the main shaft 852. Battery 832 is electrically connected to motor 1623 via telecommunications [1628]. motor function 820
The outlet of the pump 1625 of /826 communicates with the motor, in particular with the pressure storage vessel 814/890, by a channel [828] according to FIGS. 11A, B "G" or FIGS. 12A, 13A, B. In this figure, electrical output [1628] by battery 832 provides electrical communication for other functions of the motor shown in previous figures.

FIG. 15D schematically shows a process equivalent to FIG. 15C, in which the piston pump 1625 is replaced by a rotary pump 1635, communicating with said motor 1620 by a shaft 1621. The rotary pump 1635 communicates with the pressure storage vessel 814 of FIG. 13B by a channel [828]. Start motor 1623 is in communication with axle 1621 and derives its power from battery 832 via wire [1628]. The battery 832 is charged via a wire [1611] by a photo solar cell 833' and an alternator 850 and is in communication with the axle 1621. Battery 832 is connected to motor function 800 by wire [1627]. The photovoltaic cell 833' supplies H2 directly to the motor 1620 via channel [1640]. This system may preferably be used with the configurations shown in FIGS. 13F, 14B, C, D. The motor type according to FIG. 14D may be a particularly preferred embodiment.
In this figure, electrical output [1628] by battery 832 provides electrical communication for other functions of the motor shown in previous figures.

Fig. 15E shows a schematic representation of a capacitor 1641 for instantaneous storage of electricity 1642, which is charged via an electric wire [1643] and connects said capacitor 1641 to the outside of the motor (1644). Said capacitor 1641 communicates via a channel [1645] to other functions of the motor of the figures. 11A, B, C, F, G and Figs. 12A and 13A, B according to function 851 of said figures. Said functions include shafts 852, 866 and 1621, which are in communication with alternators 850 or 1624, respectively.
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 a photovoltaic solar cell 833. In addition, the capacitor 1630 is connected to the battery 832 by wires [1646] for charging.
It is connected to the.

FIG. 16A shows the scaled-up two-way actuator of FIG. 16A. The 11G-R. two-way actuator consists of two channels 3300 and 3301, each communicating from the outside to the inside of the cylinder 3302, each with a regulator controlled by a speeder 3306 via valve means 3305. (Reducing valve) Communicates with 3303 and 3304. That is, since both regulators 3303 and 3304 are in communication, one speeder 3306 can control both regulators 3303 and 3304. There are two overflow channels 3307 and 3308 communicating with each of the two spaces 3309 and 3310 on each side of the internal piston 3311. O-rings 3312 and 3313 between the piston 3311 and the actuator wall 3314.

Figure 16B shows a preliminary study of the two-way actuator of Figure 16A. It is concluded that a more quickly reacting system is one in which the piston contains an overflow channel. Furthermore, it is concluded that the regulators each need to have a stop function for that flow. The overflow channel should also have (1) an automatic contrast valve function (eg, according to Figure 210E) and (2) a check valve, respectively.
ESTV - ASYNCHONE CRANKSHAFT DESIGN - Combination of Components Figure 17A shows a complete cycle of an actuator piston in a conical chamber using ESVT. This is the same as Figures 10A-C. Although only elliptical/spherical pistons are shown, any type of expandable actuator piston may be used.

17B-H illustrate a multiple cylinder motor based on the two cylinder configuration of FIG. 17B. Figure 17B is based on the single cylinder configuration of Figure 17A where the configuration was used twice, such that the power stroke of one chamber and the return stroke (unpowered) of the other chamber were performed simultaneously.

Since the power stroke of the actuator pistons can only be performed from the second to the first longitudinal position, the two chambers face in opposite directions. As a result, the crankshaft geometry is such that the connecting rods for these actuator pistons are 180 degrees apart from each other.
3. The motor is always powered and the configuration can be used in a stand-alone two cylinder motor, or in a multiple (>2, preferably even number) cylinder motor. The flywheel may be redundant and its omission may reduce the weight of the vehicle.

Both actuator pistons can be provided with two connected sub-crankshafts (one for each actuator piston), each belonging to a different actuator piston. The communication between the closed spaces can be via channels in the sub-crankshafts and/or via channels on the outside of said crankshafts.

The closed spaces may be separated at the connection points of the sub-crankshafts (together including the crankshafts), for example, by a tightening rod 1270 (FIG. 11X) that may be arranged between the closed spaces.

With this configuration of actuator pistons, it is very possible to combine two ESVT pumps into one pump, since the increase and decrease in pressure on each actuator piston are reversed at the same time, leaving the full volume of the enclosed spaces. An ESVT pump, for example, communicates directly with one of the closed spaces, while said ESVT pump communicates indirectly with the other closed space via an external channel.

an actuator that opens and closes a connection between said ESVT pump and said enclosed space, functioning in both directions to and from each enclosed space per piston (e.g., by use of a valve actuator according to FIG. 210E or FIG. 210F); A valve may also be present. The valve may be controlled by the pressure and/or tappet of the ESVT pump and may be in communication with a camshaft (which may be in communication with a main auxiliary power line, e.g. an auxiliary H2 combustion motor); It may also be in communication with a computer (not shown).

The change in pressure within the actuator piston is when said actuator piston is in a first/second longitudinal position and a second/first longitudinal position, respectively. If the camshaft regulates the opening and closing of the actuator piston + check valve assembly, said camshaft may have a speed twice that of the shaft with which the crankshaft of the ESVT pump communicates.

The piston-chamber combination for each enclosed space in the sub-crankshaft varying the speed/pressure in the cylinder can only be used for one cylinder. These piston-chamber combinations are in communication with each other via an electric pressure regulator of a two-way actuator, which moves the respective piston rod of said piston-chamber combination and thus the external speeder. It communicates with However, it is possible to remove one of the two piston-chamber combinations and replace it by the same configuration that was used to disconnect one of the ESVT pumps, thereby allowing the piston- It is possible for the settings of the chamber combinations to be synchronized. Many valves can make the configuration vulnerable to malfunction.

Instead of a toothed belt on the power side of the auxiliary motor, where the pump is driven, it can very well be replaced by a gear wheel.
The second and third enclosed spaces may communicate with each other, for example at the connection point of the sub-crankshaft (FIG. 11W, W), for example via a movable piston (FIG. 171) that can be mounted in a channel that comprises the enclosed spaces. The piston is of dual function and therefore, for example, moves towards the second enclosed space, thereby increasing the pressure in the second enclosed space of one actuator piston, and at the same time decreasing the pressure in the third enclosed space of the other actuator piston. The dual acting piston is in fact an ESVT pump in its configuration of a motor. It is also possible to arrange the dual acting piston on the outside of the crankshaft.

A motor further comprising two cylinders, said two longitudinal positions of one cylinder being at the same geometric level of said first longitudinal position of a second cylinder, and both actuator pistons having: communicate with each other via a crankshaft, said crankshaft comprising two sub-crankshafts connected, one for each actuator piston, the connecting rods to said actuator pistons being positioned 180° relative to each other. A motor characterized by:

a motor further comprising an ESVT pump for each cylinder, the pumps being combined into one pump for the two cylinders, the sealed space of one of the actuator pistons communicating with the sealed space of the other of the actuator pistons, the sealed spaces being contained within the crankshaft, and the sealed spaces communicating with each other at a connection point of the sub-crankshaft.

The valve further includes a valve for opening and closing a connection between the ESVT pump and the second or third closed space, each connection having a check valve or non-return valve function, and the valve controlling the pressure of the ESVT pump and the second or third closed space. or a motor controlled by a tappet, said tappet communicating with a camshaft communicating with the main shaft of the auxiliary motor.

A motor further comprising two or more cylinders, each additional cylinder communicating through the enclosed space of a connected sub-crankshaft of an existing sub-crankshaft.
In FIG. 171, a two-cylinder motor is disclosed in which the enclosed spaces of each chamber in each sub-crankshaft are separated by a straight channel in which a bidirectional piston moves and communicates with each enclosed space.

In FIG. 17A, the ellipsoidal/ellipsoidal sphere actuator piston 217 is shown in a first longitudinal position. The actuator piston is expandable and operates within a chamber having different cross-sectional areas in a first longitudinal position and a second longitudinal position. The cross-sectional area and circumferential length at the second longitudinal position are smaller than the cross-sectional area and circumferential length at the first longitudinal position. Upon reaching the first longitudinal position, the actuator piston is at the end of the power stroke. During a power stroke, the actuator piston moves from a second longitudinal position to a first longitudinal position under the influence of pressurized fluid within the piston container.

The closed space in the piston reservoir, where the fluid is in constant and open communication, remains equal during the power stroke. The piston actuator's sealed space communicates with a channel in which a valve controls the volume of the sealed space. At the time of the power stroke, the valve is located closest to the actuator piston.

During the movement from the second longitudinal position to the first longitudinal position, the pressurized ellipsoidal piston 217' expands into a spherical piston 217, and the pressure in the piston gradually decreases with the expansion of the piston housing. In the first longitudinal position, the fluid in the piston is still under a small overpressure to ensure a good seal to the chamber wall. The piston 217 may be ellipsoidal in shape.

During the power stroke, if the valve position remains unchanged, the valve is retracted further away from the actuator piston. The volume of the enclosed space increases, causing the internal pressure to drop to the pressure at which the piston was fired. The fluid in the enclosed space and the piston vessel are in constant open communication with each other. Thus, if there is a pressure difference between the fluid in the piston vessel and the fluid in the enclosed space, a new equilibrium is established.

In Figure 17A, the valve moves from level "0" to "1". The depressurized production-configured piston 217", placed in the first longitudinal position, is ready for the return stroke. During the return stroke, the actuator piston assembly is repositioned in the second longitudinal position, sealing The volume of the space remains constant and the valve setting "1" is maintained. When moving from a first longitudinal position to a second longitudinal position, the piston is depressurized and released from the wall, or simply engages it, but removes the upper volume in the chamber from the volume below the piston. Do not seal. The returned piston 217"' is held by the walls of the conical chamber and maintains its shape when pressurized against the piston 217". This is achieved by changing the position of the valve.The valve is expanded from level "1" to "0" by increasing the pressure by reducing the volume of the enclosed space. The pressurized piston moves again from the second longitudinal position to the first longitudinal position, completing one complete cycle. The piston expands, lowering the internal pressure and reaching the initial piston shape 217. This movement is
It is driven by the force on the chamber wall due to overpressure in the piston and the reaction force applied in response to the actuator piston.

The main shaft to which the actuator piston is connected/mounted receives its energy from the mechanical motion, hence it is called the power stroke. Next to the valves in the channels there are various configurations to manage the pressurization and depressurization of the actuator piston.

In Fig. 17B a two-cylinder arrangement is shown. Both cylinders are identical to Fig. 17A, only the internal orientation differs by 180°. For example, the actuator piston of cylinder assembly A is at the beginning of the power stroke and the actuator piston of cylinder assembly B is at the beginning of the return stroke. In Fig. 17B this is represented by rotating the cylinder configuration by 180°, but in the motor there are several possibilities to achieve this, for example by arranging the cylinders in parallel and rotating the crankshaft connection of cylinder B more than 180° relative to the one of cylinder assembly A. The main crankshaft of the motor is composed of two sub-crankshafts, one for each cylinder-piston assembly. The cycle of the actuator piston in the conical chamber is explained in the description of Fig. 17A, while the installation of the cylinders and the processes in the motor are dealt with in Figs. 17C-H.

In Figures 17C-17H, a process description of one complete cycle of a two cylinder motor configuration is given. The disclosed two cylinder motor configuration consists of one main shaft with two sub-crankshafts, and the sealed spaces of each chamber in each sub-crankshaft are separated by a clamping rod 1270. The cylinders operate a-synchron (180 degree difference), so that when one cylinder starts its power stroke, the other cylinder starts its power stroke, as shown in Figure 17B.
As shown in FIG.

On the motor, replace one ESVT pump with an inflow/outflow connector and connect it to the remaining ESVT pumps. Valves 459/423 and 462/422 control the flow to pressurize and depressurize both pistons. For each cylinder, a set of valves is installed according to the concept of Figures 210E and 210F, one for inflow and one for fluid outflow. The valves are controlled by pressure and tappets in communication with cams on the camshaft.

The ESVT pump's crankshaft and camshaft are driven by the H2 combustion engine via a gear wheel and gear belt configuration, allowing for various speed (pre) settings. In Figure 17 C-H, the rotational speeds of the camshaft, pump crankshaft, and main shaft are the same.

The remaining ESVT pumps are of a special type in which the piston upper volume is connected to one cylinder assembly and the piston lower volume is connected to the other cylinder assembly. Since the cylinders operate asynchronously, this configuration supports the desired pressurization scheme, i.e. low pressure on one side of the ESVT pump piston for piston actuators requiring reduced pressure and for piston actuators requiring increased pressure. Provides high pressure. Special ESVT pump 8000 configurations can be used with more motor configurations and are applicable to Figures 17C-17H, for example.

Each valve set has a cam attached to the camshaft. Each cam provides two different signals during one revolution, one to the inflow valve and one to the outflow valve. The cams of each valve set are mounted identically on the camshaft, so that if the first signal is provided by the first cam, the second cam will also provide the first signal, and an additional half turn Both cams then provide a second signal. The cylinders operate asynchronously, so if the first signal from the first cam is used for the inflow valve, the first signal from the second cam is used for the outflow valve of the other cylinder assembly, and the first signal from the second cam is used for the outflow valve of the other cylinder assembly. Signal 2 is also used vice versa. Different configurations of the cam are possible as long as the cam motors the desired function of the valve.

These valves are of a special type, as described in Figure 211E. Flow is possible only when the valve piston is closed and there is overpressure in the direction of the valve actuator. The overpressure is the strength in the outflow chamber of the valve set by the spring force supporting the piston core. A channel within the valve communicates with an inlet chamber of the valve. Equal pressure in the inflow chamber and valve channel maintains the valve actuator in position and thus in the closed position. When the valve piston receives a signal by a suitable cam and closes, communication between the valve channel and the inlet chamber is interrupted. In this setting, the valve opens when overpressure occurs. At this time, when the valve piston closes, not only the communication line between the inflow chamber and the valve chamber is cut off, but also the communication channel from the valve channel to the outflow chamber is opened. The pressure in the valve channel is caused to switch from the pressure in the inflow chamber to the pressure in the outflow chamber upon closure of the valve piston. The pressure in the valve channel is in equilibrium with the outflow chamber and does not need to be overcome. Removal of the signal from the valve piston by the cam causes the valve actuator to return to its closed position, communication through the valve channel to the inflow chamber is reestablished, and communication to the outflow chamber is cut off.

The inflow valve of the valve set that controls the pressurization of the actuator has an ESVT pump on the inflow chamber side, a piston actuator attached, and a sealed space on the outflow chamber side. For outflow valves, this is the opposite. The valve piston is closed by a cam signal that is once per revolution of the camshaft. During closure of such a valve piston, fluid flow into or out of the cylinder is possible when the pressure differential across the valve is positive.

Furthermore, the motor is based on the configuration of Figure 11R, and the auxiliary power source, which is a H2 combustion engine, is according to Figure 15D.
In FIG. 17C, cylinder 800L is in the second longitudinal position and cylinder 800R is in the first longitudinal position. The ESVT pump reduces the upper volume within the cylinder and pressurizes the fluid within the channels of the cylinder assembly that makes up the 800L. By lowering the volume at the top of the ESVT pump, we increase the volume at the bottom of the 800R cylinder system and reduce the pressure. The camshaft provides a signal to the inlet valve of the channel communicating with cylinder 800L. The valve piston closes and the pressure within the valve channel is equilibrated with the pressure within the enclosed space associated with the 800L actuator piston. The pressure from the ESVT pump accumulates and becomes larger because the pressure in the enclosed space is in direct and open communication with the cylinder 800L. The overpressure causes the valve actuator to push the core pin sideways and fluid can flow toward cylinder 800L, pressurizing the piston and preparing it for the power stroke. The 800L outflow valve receives no signal, so the valve piston is open. It cannot be leaked.

The camshaft has a second cam that provides the first signal for cylinder assembly 800R. When the cylinders operate asynchronously, this first signal communication from the second cam is with the 800R outflow valve. The valve piston of the outflow valve of piston 800R is closed, thus allowing flow from the actuator piston to the ESVT pump. The 800R inlet valve receives no signal, so fluid flow towards the actuator piston is not possible. At the moment of FIG. 17C, the 800R piston actuator is in the first longitudinal position at the end of the power stroke and beginning the return stroke. The piston container is still under slight overpressure to ensure a good seal and contact with the walls. The lower end of the ESVT pump increased its volume and thus decreased the pressure. Closure of the valve piston switched valve channel communication from the actuator piston and associated enclosed space to the ESVT pump. The overall pressure situation is such that there is overpressure on the valve actuator from the actuator piston to the associated enclosed space to the ESVT pump. Flow is initialized from the piston and the enclosed space towards the ESVT pump, and this flow continues until the pressures on both sides of the valve are balanced (ignoring the small force of the spring supporting the core pin), or until the valve piston is again Continue when opening and interrupting communication.

The left side of Figure 17C shows an enlarged portion of the left side of Figure 17C.
FIG. 17C shows an enlarged section on the right side of FIG. 17C.
In Figure 17D, the motor system axle has rotated an additional 1/6 turn. In FIG. 17C, the ESVT pump has reduced the volume at the top of the piston, and in FIG. 17D, the piston remains in a position with a small volume at the top and a large volume at the bottom. Due to the rotation of the crankshaft, the fluid above the piston becomes slightly more compressed and the fluid below becomes more expanded. Also, the pressurization by the ESVT pump can split into an upper half at high pressure and a lower half at low pressure, so that a shift from one side to the other is required to indicate a change from the previous situation. is important. This upper and lower half division applies to cylinder assembly 800L, and the situation is reversed for cylinder assembly 800R. A camshaft also rotates next to the crankshaft that determines the volume of the ESVT pump. In this new situation, the cam provides no input signal to either valve. As a result, the valve piston is open and cannot flow towards or from the actuator piston and the enclosed space. Pressurization The piston within the cylinder assembly 800L moves from the second longitudinal position to the first longitudinal position by the resulting reaction force of the wall applied to the piston. During the rise, the piston expands under the influence of the internal piston pressure, maintains a good seal and contacts the walls of the chamber. The piston of assembly 800R is depressurized and moves downward without contacting or simply engaging the wall.

The left side of FIG. 17D shows an enlarged portion of the left side of FIG. 17D.
FIG. 17D right shows an enlarged portion of the right side of FIG. 17D.
In FIG. 17E, the piston of the cylinder assembly 800L reaches a first longitudinal position, which is the end of the power stroke. The actuator piston of the cylinder assembly 800R is still depressurized and reaches a second longitudinal position, which is the end of the return stroke. The various shafts have rotated another 60 degrees. The piston of 800L is still under a slight overpressure to ensure a maximal expansion into the chamber and a good seal to the wall. The pressure in the piston 800L, and therefore in the channel communicating with the piston 800L, is at its lowest value of the power stroke at its highest position in the chamber (or first longitudinal position). The camshaft does not provide a signal to the valve, therefore the valve piston is open and no inflow or outflow is possible. The ESVT pump, driven by the connector to the crankshaft, is still oriented so that the volume above the piston of the ESVT pump is at a minimum, resulting in high pressure, while the volume below the piston remains large at low pressure.

During the first half of the process of Figures 17C-17E, the piston actuator of cylinder 800L executes a power stroke, providing power to the main shaft. The main shaft rotates at the same speed as the crankshaft and camshafts. The piston actuator of 800R moves only from a first longitudinal position to a second longitudinal position with minimal work cost. This necessary work is provided by the main shaft. Other elements requiring energy are powered by auxiliary power sources, such as the crankshaft and camshafts.

The left side of FIG. 17E shows an enlarged portion of the left side of FIG. 17E.
FIG. 17E shows an enlarged portion on the right side of FIG. 17E.
In FIG. 17F, the cam on the camshaft again provides a signal. The camshaft has rotated further, now more than 180 degrees relative to the start-up state of FIG. 17C. The signal by the cam is another one as active in FIG. 17C. The signal closes the valve piston of the outlet valve of cylinder 800L. The pressure in the valve channel is equal to the slight overpressure in the piston actuator at the end of the power stroke. By closing the valve piston, the valve channel exchanges fluid with the ESVT pump, balancing these two pressures. The ESVT pump piston is making a stroke that increases the volume above the piston and thus reduces the pressure in this space. The slight overpressure of the piston actuator 800L has a positive pressure difference with respect to the pressure in the valve outlet chamber, equal to the pressure at the top of the ESVT pump. The positive pressure difference moves the valve actuator, pushing the core pin to the side and allowing the flow of fluid from the actuator piston to the ESVT pump. This decompresses the piston and prepares it for the return stroke. On the return stroke, the piston must be away from the wall or simply engaged. The valve piston of the 800L inlet valve does not receive a signal to keep the cam open, so no flow passes through the valve.

For the valve set that controls the pressurization of the piston and the associated enclosed space of the 800R,
The signal from the cam closes the valve piston of the inlet valve. The valve piston of the outflow valve remains open and therefore does not facilitate flow from the piston to the ESVT pump. Closing the valve piston of the inlet valve communicates the pressure in the valve channel with the depressurized internal volume of the piston, just completing the return stroke to the second vertical position. As the ESVT pump stroked, the volume under the piston of the ESVT pump decreased and the fluid within this volume became pressurized. The pressurized fluid within the ESVT pump with which cylinder assembly 800R communicates creates a positive pressure differential across the valve actuator. This pressure differential allows flow from the ESVT pump to the actuator piston and associated enclosed space. We want to hold the piston container under pressure and thus expand it, but since the outside of the piston is held against the walls of the conical chamber, we instead exert a force on the walls, creating a reaction force on the piston. This reaction force has a component in the longitudinal direction of the chamber and drives the piston. Therefore, by pressurizing the 800R piston, you can perform a power stroke in the near future.

In Figure 17F, the status of cylinder assemblies 800L and 800R is that of the other cylinder assemblies in the previous half cycle of Figure 17C. Pressures, valve settings, longitudinal positions, etc. are equivalent to those shown in Figure 17C for other pistons to operate the motor smoothly.

The left side of FIG. 17F shows an enlarged portion of the left side of FIG. 17F.
FIG. 17F is an enlarged view of the right side of FIG. 17F.
In Figures 17G and 17H, the axle rotates further every sixth revolution, completing the cycle. The cams on the camshaft do not emit a signal in these two steps. Thus, the valve pistons of the inlet and outlet valves of both valve sets remain open. When the valve pistons open, the pressure pushing on the actuator valve from the inlet chamber of each valve is countered by the constant valve channel pressure.

When the valve actuator in communication with the inlet chamber of the valve remains in place, no flow occurs between the ESVT pump and the piston actuator.
Also, the ESVT pump settings remain the same as in FIG. 17F. The volume above the piston of the ESVT pump remains large, resulting in a low pressure at the top of the fluid, which is in communication with cylinder assembly 800L. Also, the volume below the piston, which is in communication with cylinder assembly 800R, remains small, resulting in a high pressure. Since there is no fluid flow in FIG. 17G, H has no further meaning, but for the transition from FIG. 17H to FIG. 17C again, it is the pressure change due to the return stroke of the piston in the ESVT pump that is important to create the appropriate valve positive pressure differential.

In FIG. 17G, the piston assembly 800L is moving 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 unpressurized and is free from or merely engages the walls of the chamber. At the same time, the cylinder assembly 800R is performing a power stroke from the second longitudinal position to the first longitudinal position. This causes the pressurized piston to expand, reducing the internal pressure and maintaining good contact with the walls of the conical chamber.

In FIG. 17H, the piston actuator of assembly 800L completes its return stroke and reaches the small end of the conical chamber. Here, the cross-sectional area and circumferential length are minimum. The pressurized actuator piston of cylinder assembly 800R reaches a first longitudinal position where the piston expands maximally at the large end of the conical chamber and has a large cross-sectional area and maximum circumferential length. Until the last movement of the power stroke, some overpressure remains in the piston to ensure a good seal to the wall. At this point, the wall normal direction is perpendicular or nearly perpendicular to the longitudinal axis of the chamber.

FIG. 17G on the left shows an enlarged portion of the left side of FIG. 17G.
FIG. 17G Right shows an enlarged portion of the right side of FIG. 17G.
FIG. 17H Left shows an enlarged portion of the left side of FIG. 1TH.

Figure 17H right shows an enlarged portion of the right side of Figure 17H.
The next step in the ongoing operation of the motor is again the same as in Figure 17C. Therefore, this cycle of six intermediate steps in Figures 17C-H represents a full cycle of a motor that includes two cylinders operating asynchronously.

FIG. 171 shows an example of the appearance when an ESVT pump is installed at the connection between two sub-crankshafts. The motor elements are identical to the motors described in Figures 17C-17H. ESVT pumps can be operated by a mechanism in a cylinder along the axis of the crankshaft, such as a worm wheel or spring mounting. The piston within the straight channel forming the ESVT pump may also be driven by an external system. The bidirectional piston is moving within the chamber, thereby expanding the volume of the closed region it moves away from and decreasing the volume of the closed region it approaches. Decrease and increase the pressure in a closed space, respectively. The piston seals both sealing areas simultaneously.
ESTV - SYNCHRONE CRANKSHAFT DESIGN - Combination of Components Figures 18A-18G illustrate multiple cylinder motors based on a two cylinder configuration, based on the two cylinder configuration of Figure 18A, which is based on the one cylinder configuration of Figure 17A with reference to Figure 10. However, any expandable actuator piston type can be used.

Figure 18A shows two cylinders with their output strokes coupled simultaneously in time, with both actuator pistons communicating with each other via a crankshaft (which may include two sub-crankshafts) and the connecting rods to these actuator pistons positioned at 0° with respect to each other.

This is done by the configuration of two identical piston-chamber combinations, where the second longitudinal position of one cylinder is at the same geometric level as the second longitudinal position of the second cylinder. The return stroke is therefore not powered, and such a configuration can be combined with other configurations (motors containing two or more cylinders) to fill the power gap in the return stroke. Another solution is the use of a flywheel.

The ESVT pump is a pump that combines two cylinders into one pump by connecting the closed space of the actuator piston, for example, the connection point of the sub-crankshaft.
It can be made into one pump.

If another group of actuator pistons is added to said motor and the stroke of the added piston-chamber combination is the same as the stroke of said motor;
Unlike the configuration of Figure 18, one ESVT pump can be used for the entire group, preferably one piston-chamber combination for pressure/speed control, as well as one piston-chamber combination. can be used for the entire combination of

If another group of actuator pistons is added to said motor and the stroke of the added piston-chamber combination is opposite to the stroke of said motor, then one ESVT- Pumps can be used for entire groups of piston-chamber combinations in combination with external channels, and for bidirectional check valves and valve actuators (see FIGS. 17C-17H (inclusive)) . The two crankshafts of both groups of piston-chamber combinations may be in communication with each other, whereby the internal channel of each crankshaft is preferably filled with a filler, e.g. 1270). A power balance can be generated in the motor, whereby power locks of the various actuator pistons are configured such that the motor provides constant power.

In Figures 18B-18G, the motor pressurization scheme during one cycle is disclosed. The motor is
As shown in Figure 18A, it has a two cylinder configuration. The piston actuators of each cylinder assembly are consecutive at the same stage of the cycle, and the piston actuators operate in parallel.

The motor is also based on Fig. 11R, and the motors of Fig. 17C-17H were based on this concept, so the main difference is in the piston pressurization. The auxiliary power source is an H2 combustion engine with forced cooling of the liquid. The auxiliary power provides work for the pump, the battery and the crankshaft.

Two piston actuators mounted on the crankshaft are connected to one ESVT pump. Since the pressure schemes of both pistons are equal, the pressure settings of the ESVT pump required by the piston actuators are the same. This allows the two ESVT pumps for each actuator piston to be simply combined independently into a single shared ESVT pump 1055, allowing only this size to be matched. Next to the ESVT pump, one piston-chamber combination 1050 is installed for pressure/speed control of this two cylinder configuration. Communication between the two actuator pistons takes place at the connection of the two subrank axes, and the second and third closed spaces are connected, as disclosed in FIG. 11 W or W.

No valves are installed between the ESVT pump and the sealed spaces or piston actuators of assemblies 800L and 800R. To interrupt the connection between the ESVT pump and the actuator pistons, the connectors include holes that allow fluid flow toward or from the ESVT pump, or block this communication and set the amount of fluid in the sealed spaces and associated pistons. An example of such a facilitated connection between the actuator piston assembly and the crankshaft with the sealed spaces is shown in Figure 11T.

In Figure 18B, the communication line from the enclosed space in the subrank shaft to the associated piston actuator is open, allowing fluid flow. The actuator piston has just completed a return stroke and is in a second longitudinal position. The crankshaft of the ESVT pump generated an upward stroke to reduce the volume within the chamber and increase the pressure of the fluid within the ESVT pump. When the communication line to the actuator piston is opened, pressurized fluid can flow into the depressurized actuator piston. During the return stroke, the pressure in the actuator is reduced so that it does not touch or engage the wall, as well as sealing the volume in the chamber below the piston from the volume above. Also, as the ESVT pump pressure increases with the piston actuator pressure, high pressure fluid flows into the piston actuator. The pressurization of the actuator piston establishes a good contact with the chamber wall, the overpressure tends to expand the piston-actuator, which is prevented by the chamber wall, but the reaction force causes the piston-actuator to move in the first longitudinal direction. It will move upward towards the position.

The left side of Figure 18B shows an enlarged portion of the left side of Figure 18B.
Figure 18B shows an enlarged section on the right side of Figure 18B.
In Figure 18C, the piston actuator is halfway through the motor's power stroke and the motor crankshaft is rotating upward. Since the piston actuators move synchronously, the situation for both cylinder assemblies is equal. The motor crankshaft further closes the communication line between the piston actuator and the enclosed space within the sub-rank shaft and is in constant open communication with the ESVT pump. The overpressure causes the piston to expand into the enlarged area of the conical chamber. Since there is no communication with the ESVT pump and the internal volume increases, the internal pressure of the piston decreases. ESVT pumps keep the volume in the chamber small and maintain high pressure in the connected system.

The left side of Figure 18C shows an enlarged portion of the left side of Figure 18C.
The right side of Figure 18C shows an enlarged section of the right side of Figure 18C.
In Figure 18D, the piston actuator has reached the end of its power stroke. The piston expanded to its maximum within the conical chamber. The piston moved to a first longitudinal position within the chamber. Although the volume of the actuator piston has increased, the fluid within the piston is slightly overpressured to establish good contact with the chamber wall for the entire power stroke. The crankshaft of the motor to which the piston is connected rotates half a revolution relative to the starting condition of Figure 18B. The hole in the connector from the piston rod to the enclosed space of the sub-rank shaft is closed, so that the enclosed space of the sub-rank shaft is connected, and therefore between the piston actuator fluid and the ESVT pump or other piston actuator. There is no communication between the two. The amount of fluid in the piston remains unchanged. The fluid in the ESVT pump is brought to high pressure by a small volume within the chamber.

The left side of FIG. 18D shows an enlarged portion of the left side of FIG. 18D.
FIG. 18D Right shows an enlarged portion of the right side of FIG. 18D.
In FIG. 18E, the crankshaft of the motor rotates a little further, which opens a hole between the sealed space in the crankshaft and the piston rod, allowing the flow of fluid. The crankshaft of the ESVT pump is in a stroke that moves the connected piston of the ESVT pump away from the outlet of the pump chamber, expanding the volume of the ESVT pump and reducing the pressure. The pressure drop of the ESVT pump is smaller due to the smaller overpressure of the piston, as a result of which the fluid from the piston flows out in the direction of the ESVT pump, depressurizing the piston. By releasing the internal pressure, the shape of the piston changes from the shape of a sphere-ellipsoid that contacts the wall in the first longitudinal position to the shape of an ellipsoid without a wall or just engaging with it. Also, the piston may be of a different shape with an accompanying shape scheme that may differ from this one. The piston actuators of both cylinder assemblies 800L and 800R are at the beginning of the return stroke.

The left side of FIG. 18E shows an enlarged portion of the left side of FIG. 18E.
The right side of FIG. 18E shows an enlarged portion of the right side of FIG. 18E.
In FIG. 18F, the actuator pistons 800L and 800R are in the middle of the return stroke. The motor crankshaft is moving downwards, working to move the depressurized cylinder from a first vertical position to a second vertical position. The actuator pistons remain depressurized when communication in the connector is again cut off. The amount of fluid in the piston system remains constant, and if the volume is the same, the pressure is also constant. The pistons maintain the shape they have at the end of the stage shown in FIG. 18E. The volume of the chamber in the ESVT pump is still large so that closing the communication to the pistons upwards causes the fluid in the pistons to flow in the direction of the ESVT pump.

The left side of Figure 18F shows an enlarged portion of the left side of Figure 18F.
The right side of FIG. 18F is an enlarged view of the right side of FIG. 18F.
In FIG. 18G, the piston actuator has completed the cycle and reached the second longitudinal position. The ESVT pump is again slightly reducing the volume within the chamber, but the pressure remains low. Additionally, the communication hole between the ESVT pump and the actuator piston is also closed. During the power stroke, the piston actuator performs work on the crankshaft for the power connected system, but during the return stroke of both piston actuators, the crankshaft provides work to move the piston actuators. As a result, the power supply by the motor is not constant.

The left side of Figure 18G shows an enlarged portion of the left side of Figure 18G. The right side of FIG. 18G is an enlarged view of the right side of FIG. 18G.
CRANKSHAFT DESIGN - Combination of Components Figure 19A shows one cylinder motor based on Figures 11B, 11C, where some parts are further considered and the auxiliary power source is, for example, H20 is selected as the combustion motor to burn H2, which is derived from the electrolysis of Reservoir 1612 may be filled with H2O 1613 through filler opening 1614 by an external source. H2O from the water reservoir may be transported to container 1616 by channel [1615]. The power required to perform electrolysis 1617 within the vessel is provided by a communication line [1069] in contact with battery 832. Battery 832 can be charged by solar cell 833 and receive energy by alternator 850. The alternator communicates with the motor's main crankshaft 852 by a toothed belt and gear wheel. The battery can provide a signal to electric starting motor 830. Another communication line [1064] from the battery may provide input to a pressure reducing valve 840 that connects the second enclosed space inflow connector of the piston cylinder assembly 800L from the pressure storage vessel 814 through channel 829. Control the flow of fluid to. The setting of check valve 840 is controlled by speeder 841. The output H2 of the electrolysis process is supplied to the combustion engine 3525 by channel [3545]. Optionally, O2 is transported to the combustion engine 3525 by a separate channel [3546]. In the engine, under the control of signals by a communication line [1069], H2 and O2 are processed during the production of water, which can be fed back to the water reservoir 1612 (not shown). The combustion engine can also generate heat that can be conducted by a heat exchanger and used for secondary applications outside of this motor. A combustion engine powers the shaft. This piston pump 826 is connected. Said piston pump pressurizes fluid coming by channel [825] from the outflow connector on the crankshaft and is connected to the third enclosed space of the cylinder assembly. The free end of crankshaft 852 can be connected to a flywheel 835, clutch 836, or gear wheel 837 (not shown).

The piston assembly 800L operates according to the consumption technique described in FIG. 11A. The fluid in the second sealed space in the crankshaft is at the pressure of the pressure storage container 814 or at a reduced pressure after passing through the pressure reducing valve 840, while the channel [825] connected to the outlet connector is at a lower pressure, but the pressure can be different due to a one-way valve at the end of said channel that controls the positive pressure difference relative to the pressure of the piston pump 826. The piston actuator is connected to the crankshaft using a connector described in FIG. 11D. The second and third sealed spaces do not communicate with each other because the channels are interrupted in the connector. The connector allows the flow of fluid from the second sealed space with the piston actuator in the second longitudinal position. Also, when the piston assembly is in the first closed position, it is between the third closed position and the piston actuator. In the first longitudinal position, the slight overpressure still present in the actuator piston establishes the flow of fluid into the third sealed space due to the lower pressure in the channel [825]. The piston is depressurized and disengaged from or merely engaged with the walls of the chamber, not sealing the volume above the piston from the volume below. During the return stroke, the rotation of the crankshaft 852 closes the communication between the second and third sealed spaces with the piston actuator. Then, when the piston reaches the second closed space, the communication with the second closed space is opened. The actuator piston is depressurized and the second sealed space is pressurized by the pressure storage vessel and the pressure reducing valve, so that the fluid flow is in the direction of the actuator piston. The pressurized piston expands in the chamber and receives a reaction force due to the force on the walls. This force drives the actuator piston upward to a first longitudinal position. The expansion of the piston and the movement to the first longitudinal position is the power stroke.

FIG. 19B shows a two cylinder motor according to FIG. 19A with consumption technology, the two cylinders being arranged specularly on the center line of the sub-crankshaft connection. The third closed spaces (outlets) of the two piston actuators 800L and 800R communicate with each other via the connection of the two sub-crankshafts, and the second closed spaces (inlets) communicate with each other externally. The cage (with a check valve) and the crankshaft (consisting of two sub-crankshafts) are arranged so that the power stroke of each actuator piston moves in the same (0°) direction (synchronously) according to the principle of Figure 18A. Designed to.

If more than two cylinders are required for the motor according to this synchronization principle, more cylinders may be added, for example, for the connection to the second enclosed space of the added cylinder another second enclosed space is connected to the unused end, so that a three-cylinder motor is produced. The free third enclosed space of the added cylinder can be connected to the third enclosed space of another added cylinder, so that the motor works with four cylinders. The currently shown closed ends of the channels of the sub-crankshafts may need to be opened, rather than opened, in order to establish communication between the closed spaces with equal pressure schemes.

The left side of FIG. 19B shows an enlargement of the left portion of FIG. 19B.
FIG. 19B right shows an enlargement of the right side portion of FIG. 19B.
FIG. 19C shows a two cylinder motor based on FIG. 19A, which is in a pressurization process comparable to FIG. 19B. FIG. 19C shows that the configuration of the motor with synchronously operating pistons can be different from the motor in which the pistons are installed in the same direction (0°). In the configuration of FIG. 19C, the power strokes of the piston actuators occur at the same moment, but the orientation of the actuator piston 800L is rotated by more than 180°. Both of said reorientations are connected to the crankshaft as in the direction of the conical chamber into which the piston actuators are inserted, so that the power strokes are oriented in the opposite direction. Each second closed space in the sub-crankshaft is connected to the pressure storage vessel by a channel [829], and the closed spaces are in communication with each other by an external channel [825]. The third closed spaces are in communication with each other through an external channel that facilitates the flow from the actuator pistons to the piston pump. Upon connection of the two sub-crankshafts, the closed spaces are interrupted and the piston assembly 800L
There is no communication between the and the 800R.

FIG. 19C left shows an enlargement of the left portion of FIG. 19C.
FIG. 19C right shows an enlargement of the right portion of FIG. 19C.
FIG. 19D shows two cylinder motors according to FIG. 19A, with the piston actuators operating asynchronously. When piston assembly 800L begins on the return stroke, piston assembly 800R begins on the power stroke. Therefore, the other piston actuator
When the first piston actuator is in the second longitudinal position, one piston actuator is in the second longitudinal position, and vice versa. The actuator piston is oriented in the opposite direction (180°). Since there is always a power stroke and a return stroke, the power from the 19D motor is
It is continuous and at a relatively constant level. The sealed spaces of each cylinder assembly are not connected via the sub-crankshaft, and the pressurized channel [829] communicates with both second sealed spaces. Channel between 3rd channel [825]
The enclosed space also communicates with piston pump 826. The opening of the connector from the second or third confined space to the actuator piston differs by half a cycle between piston assemblies 800L and 800R, so that communication through the pressure channel between the piston assemblies is limited to the closed space. Limited. Channels [825] and [829] are external since there is no communication via connections between sub-crankshafts.

The left side of FIG. 19D shows an enlargement of the left portion of FIG. 19D.
FIG. 19D right shows an enlargement of the right portion of FIG. 19D.
Instead of a toothed belt on the power side of the motor, where the pump is driven, it is very well replaced by a gear.
19620 Description of the Preferred Embodiment FIG. 21A shows a so-called constant maximum force chamber 1 with a longitudinal section wall 2 in a first longitudinal position of the piston (not shown) parallel to the central axis 3. Part 4 of the chamber wall has a convexly formed wall of the longitudinal section of chamber 1 . A transition section of the longitudinal section of the outer wall of the chamber from a convex wall section 4 to a concave wall section 5 A wall section 6 arranged in the second longitudinal position of the piston (not shown) is connected to the central axis 3 of the chamber 1. not parallel to. The common boundary 9 of the longitudinal section 10 of the chamber 1 is the first
is the longitudinal position at which one bar overpressure is reached by a piston (not shown) when moving from a longitudinal position to a second longitudinal position. Common boundaries between longitudinal section sections 12/14/16/18/20/24/26/28/30 of chamber 11/13/15/17/19/21/23/25 and 27 respectively , 1/2/3/4/5/5/6/7/8/9/10 bar overpressure relative to atmospheric pressure in a modern bicycle pump was reached by a piston (not shown) at a longitudinal position of 1/2/3/4/5/5/6/7/8/9/10 bar. The inner walls of longitudinal section sections 28, 29, 30, 31, 32, 33, 34, 35 and 6 are convex, while the inner walls of longitudinal section 7 are It is concave (6-7 bars). The dashed line shows the outline of the room (36-37-38) according to the formula. This is by design to avoid making the room look top-heavy. Since this adaptation is taking place at the beginning of the hyperbolic function (the acting force on the piston as a result of the longitudinal shape of the chamber, measured from the first longitudinal position to the second longitudinal position) , such adaptation does not affect the maximum actuation force. This also applies to the outer wall in longitudinal section (unnumbered), since the wall thickness is small and constant in size over the entire length of the chamber: see WO/2008/025391.

The longitudinal position of the common boundary may be mathematically determined as a result of the remaining volume of the stroke volume of the conical chamber under the piston and the maximum value of the pressure, which in this figure is 10 bar. What is characteristic is that the distance between the successive common boundaries from the first longitudinal position of the piston to the second piston position is smaller the higher the overpressure rate. This is different from the case of the height of the walls of the longitudinal sections 28, 29, 30, 31, 32, 33, 34, 35, 6, 7. The position of the walls at the common boundary is based on the selected value of the maximum applied force, in this case 250 kgf (250 N). As a result, the characteristic shape 1 of the chamber is obtained (WO/2008/025391).

FIG. 21B shows the shape 1 of the 10 bar (overpressure) chamber of FIG. 21 (continuous lines) and the shape of the 16 bar (overpressure) chamber (dashed lines) for the same length of the chamber. If the transition dimension of the inner diameter of the part 30 creates problems for the piston dimensions, a recalculation of the chamber dimensions may be done with the maximum value of the overpressure unchanged by increasing the maximum value of the working force. This would result in, for example, a larger diameter of the reference number 30. The wall thickness is approximately uniform over the length of the chamber, but in said recess 7, the thickness may be a little larger than the wall thickness of the remaining walls. If the maximum overpressure is greater than 10 Bar (for example 16 Bar), a recalculation can be done. This can be achieved by choosing a higher maximum working force so that the circumference of the cross section is larger. This means that the conical outer wall of the chamber can approach a second longitudinal position before the circumference reaches a minimum to ensure that no jamming occurs, as defined by the type of piston. Near the first longitudinal position, the calculation is done verbatim, the size of the chamber becomes too large. Therefore, the shape of the chamber can be defined so that the circumference is smaller. The same is true for other common boundaries.

The task of optimizing the chamber for the demands on the hand pump can be performed in a manner similar to that described above. The problem to be solved here is the minimum dimension of the outer circumference of the inner wall of the chamber (
(depending on the performance of the piston), the maximum dimension of the chamber circumference in the first longitudinal position where the user is holding the handle, and the specified maximum applied force.

Figure 22A shows the bottom of the chamber of the improved bicycle floor pump where the bottom of chamber 1 of Figure 21 can also be seen. Chamber 1 is attached to foot 41. Flexible manchette 42 assembles chamber 1 on foot 41. The hose 43 connected to the outlet 44 of the pressure expansion vessel 49 has no check valve at this outlet. A piston 45 (schematically depicted) comprises a piston rod 46. A check valve 47 is arranged at the bottom of the piston rod, communicating with the external atmosphere (48), so as to fill the chamber 1 when the piston 45 moves from the second longitudinal position to the first longitudinal position. It opens towards chamber 1. An expansion pressure vessel 49 is shown having a chamber 56 and is equipped with an inlet check valve 50 which, when opened, communicates the chamber 1 with the hose 43 via the outlet 44. Cross section of the outer wall 51 of the inflation pressure vessel 49 with the inner wall 52. An expansion pressure vessel 49 is assembled between the upper end 53 and lower end 54 of said vessel 49. The top end 53 of the inflation pressure vessel 49 is sealed to the wall surface of the chamber 1 by an O-ring 55, and the top end 53 and bottom end 54 are sealed to the wall surface 52 of the inflation pressure vessel 49 by gas seal screws 58 and 59, respectively.

This is the preferred embodiment for very high pressures (e.g. 16 bar) and when it is difficult for the piston to seal to the inner chamber wall. This avoids the transition of the seal from the longitudinal section of the convex wall to the longitudinal section of the concave wall (see Figure 1).

Figure 23 shows another constant pressure chamber 80 with a maximum pressure of 10 bar with the same specifications as the chamber in Figure 1, except that the pressurized vessel type piston must ensure that it does not move in the second longitudinal piston position. It shows.

The transition from said convex wall 82 of the longitudinal section between common boundaries 83 and 84, corresponding to an overpressure of 0 bar and 7 bar, respectively, to said wall 81 parallel to the central axis 85 of the chamber 80 Containing smaller internal concave subsections 86.1, 86.2 and 86.3 respectively between the boundaries 84, with a special internal concavity 86 corresponding to an overpressure of 7 bar to the common boundary 88 for an overpressure of 10 bar . The shape of the inner wall of said chamber and its outer wall no longer have to correspond to each other; between the common boundary 84 in the case of an overpressure of 7 bars and the common boundary 88 in the case of an overpressure of 10 bars, the outer wall It is still convex and the inner wall is concave. This difference in shape makes it possible to increase the wall thickness relative to the remaining wall thickness of the chamber with the weakest spot of the chamber, ie the transition from the concave inner wall section to the inner wall parallel to the central axis of said chamber. an outer wall 89 of the chamber located where the inner wall of the chamber is present;
The straight line may be selected to be parallel to the central axis of the chamber, but not necessarily parallel to the central axis. This can be done for aesthetic purposes, as the curved shape provides some visual tension.

The transition from the concave inner wall of the chamber parallel to the central axis of the chamber to the inner wall may be smooth so that the piston can pass through this transition without disturbing it.

FIG. 24 shows a foot 70 of an improved floor pump, for example for tire inflation. A flexible cuff 71 holds the conically shaped 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. Expandable piston 73 Enclosed space 66. Tube 65 inlet check valve 75. Outlet check valve 76. Hose 77. Measuring spaces 78, 79 (inside the hose). Valve connector 67 (not shown). The space 68 within the valve connector 67 is also part of the measurement space (not shown).

FIG. 25 shows a chamber 100, which is a 10 bar overpressure chamber of the chamber 1 of FIG. 21. It is in a second longitudinal position and ends at the common border 27. This bottom of this chamber is screwed into the bottom 101 corresponding to the longitudinal section 30 of FIG. 21. The screw connecting both parts of the chamber is a gas screw 102, which provides a gas-tight connection. At the bottom 103 of the chamber part 100 there is an outlet 104 into which a hose nipple 105 is screwed. The chamber part 100 is equipped with a piston 106, which is depicted diagrammatically. The piston 106 is equipped with a hollow piston rod 107, which is equipped with a non-return valve 108, which opens the space 109 between the piston and the bottom part 103, thereby allowing air to flow from the atmosphere (48) into said space 109. On the hose nipple 105 there is a hose 110 assembled with a hose clamp 111. The other end of the hose is connected, for example, to a valve connector 67. Hole 112 in hose 110.
Description of the preferred embodiment of the design of the 19630 circular ionization chamber Figure 30A shows the circular chamber of Figure 12B with a piston moving in a non-moving chamber. The circular subchamber 961 has a center point 980 of a circular section line 981 closest to the center point 967 of the circular chamber 960. This center point 980 is in a quadrant 982 before the quadrant 983 in which the line 981 lies. A radial line 987 between the circle center 980 and the circular section line 981. The circular section line 984 of the circular subchamber 961 is the furthest to the center point 967 of the circular chamber 960 and has a center point 985 in the quadrant after the line 984 lies. A radial line 988 between the circle center 985 and the circular section line 984. This may be valid for all other subchambers 962, 963 and 964. The circular section line may be a circular section line in other preferred embodiments.

FIG. 30B shows the circular chamber of FIGS. 13C and 14D without the piston moving. Here we have a circular chamber and subchamber design identical to the design of Figure 30A.

FIG. 31A shows FIG. 14D through the central axis 1750 of the chamber 1749, indicated by section XX.
FIG. 31B shows a scaled-up detail of section XX of chamber 1749 of FIG. 31A.
Chamber walls 1785 are shown in Section XX. Walls 1785 and chambers 1749 respectively
ducts 1786, 1787, 1788, 1789, 1790, 1791, 1792, 1793, 1794, 1795, 1796, and 1797 having openings to. Preferably there are no ducts in the vicinity of the section.

X-X corresponds to the section farthest from the center 1750 of the circular chamber 1749. From there, the ducts from the periphery of the chamber 1749, on both sides of the line of section X-X (1786/7/8/9/90/91, and 1796/5/4/3/2/1), are ducts of increasing width, duct 1791 having the greatest width. Said ducts are meant to reduce the size of the contact area between the piston and the wall 1785 of the chamber 1749, to guide the piston through the circular chamber towards the circular chamber, and for said ducts to obtain a suitable thrust, which may be equal to the circumference of the circumference of the contact area between the piston and the wall 1785 in said chamber 1749.

FIG. 32(a) shows that the chamber wall and a plane orthogonal to the base circle intersect in a circle whose centre is on the base circle.
FIG. 32(B) shows a cross section of the piston boundary.

Figure 32(C) shows the geometry of the cap, ie, the area and internal volume of the cap, requiring only the values of a and h. Regarding this, please refer to equations (2.1) and (2.2). The radius of the virtual sphere is shown in equation (2.3).

Figure 32D shows a piston with an end cap.
Figure 32E shows a piston with an end cap within a transparent Fermi tube hamper.
Figure 32F shows the pure contact area between the piston and the chamber, visible inside the transparent chamber wall.

FIG. 32G shows the contact area between the piston and the chamber.
Figure 32H shows the cross section of the chamber wall. The chamber reaction forces are marked in grey (1800).
The sum of the forces acting on the cross section is perpendicular to the chamber wall. For a cross section, the force value is proportional to the (variable) longitudinal length of the cross section shown and the internal pressure of the piston.

The local reaction force from the chamber wall is proportional to the longitudinal width of the cross section, which is also linear with the distance to the center of the central circle, i.e., at the origin. At first order, the circumference of the cross section varies like a tube of constant radius; its length depends linearly on the distance to the origin. The local force varies accordingly, and is therefore adjusted to drive the entire wall, and therefore the piston, as a pure rotation about the origin. Fermi structure. The generator circle has orthogonal planes at each point, as shown. The chamber wall intersects all such orthogonal planes in a circle whose center is the generator circle. The chamber wall is a "cone" when the radius of said circle in the orthogonal planes is chosen to have a linear (or simply increasing) value as a function of the arc length along the generator circle.

FIG. 321 shows the section of FIG. 32H with an additional section to provide an open view.
FIG. 32J shows FIG. 32H, where the red (1801) vector is the component of the vertical gray force (1800).

Figure 32K shows Figure 32J with an additional section to provide an open view.
Figure 32(L) shows Figure 32(J). In Figure 32(J), the actual sliding force along the wall surface is shown in blue (1802). This is the projection of the red (1801) vector at right angles to the chamber wall.

FIG. 32M shows FIG. 32L with an additional section to provide an open view.
19640 Description of the Preferred Embodiments Figure 40A shows a longitudinal section of a pump 1500 having a piston 1501 with a U-shaped support means 1502, an O-ring 1503 and a flexible impermeable layer 1504, finally supported by a foam 1505 at a first longitudinal position in a chamber 1506. The support means 1502 is rotatably fixed to a piston rod 1507 by a suspension 1508 with an axis 1510. A tension spring 1509 is fixed to the piston rod 1507 above the axis 1510, the other end being on the support means 1502 closer to the O-ring 1503. A horizontally arranged spring 1511 supports the O-ring 1503. The barrier flexible sheet 1504 includes a layer 1512 with a reinforcement 1514 (only shown in Figures 40B, 4 ID, 4 IE) vulcanized on the layer without the reinforcement 1513. The chamber 1506
The central axis 1518 of the chamber 1506. The angle a between the line connecting the center of the axis 1510 to the center of the O-ring 1503 and the central axis 1518. The impermeable flexible sheet is perpendicular to the central axis 1518 of the chamber 1506 without being stressed by loads from the fluid in the chamber 1506.

FIG. 40B shows that an impermeable flexible sheet 1504 is vulcanized within an O-ring 1503 .
The layer 1513 without reconditioning and the layer 1512 with the reinforcement 1515 are vulcanized together. The support means 1502 and the horizontal spring 1511 are vulcanized onto the O-ring 1503 and the layer 1513 of the impermeable sheet 1504. The end of the support means 1502 has a slightly bent flat surface 1516, which fits the shape of the O-ring 1503 during manufacture. The O-ring 1503 is squeezed onto the wall 1517 of the chamber 1506.

FIG. 40C shows a longitudinal cross-section of the piston of FIG. 40A in a second longitudinal position. Piston rod 1507, which is the central axis 1518 of chamber 1506, has a wall 1517. The support means 1502 was rotated about the axis 1510 and the form 1505' was squeezed. Spring 1509' was pulled longer. O-ring 1503 has increased in size and is still squeezed against wall 1517 of chamber 1506. The water-shielding sheet 1504' has increased in thickness, and the horizontal spring 1511' has been tightened together. Angle β between the line connecting the center of shaft 1510 and the center of O-ring 1503 and central axis 1518.

FIG. 41A shows a top view and a cross-sectional view of the piston 1501 of FIG. 40A.
Chamber 1506 is from a first vertical position. Wall 1517 of chamber 1506. Piston rod 1507. Support suspension 1508 means 1502. Axis 1510. Tension spring 1509 of support means 1502.

FIG. 41B shows details of the suspension of the support means 1502 on the O-ring 1503 and lying spring 1511 of the piston 1501 of FIG. 40A. A small curved flat surface 1516 at the end of the support means 1502 is vulcanized onto the O-ring 1503. The end 1519 of the support means 1502 has a notch 1521 that matches the size and shape of the horizontally lying spring 1511. The border 1520 of said spring 1511 is only partially visible at the end of the support means 1502.

FIG. 41C shows a cross section of chamber 1506 with piston 1501 shown.
40A in a second longitudinal position. The suspension 1508 of the support means 1502.
41D shows spiral reinforcements 1522, 1523, 1524 of a flexible impermeable sheet 1504, the material being flexible. These spirals are drawn approximately concentrically with each other at a fixed distance around the central axis 1518 of the chamber 1506. Other configurations may be possible, for example two layers with rebars that may cross each other at a small angle, but are not shown.

FIG. 41E shows another reinforcing configuration, namely a more or less elastic reinforcing member 1525, located concentrically about the central axis 1518 of the chamber 1506.
FIG. 42A shows a longitudinal cross-section of a piston 1530 comprising a support means 1502, an O-ring 1503 and a flexible impermeable sheet 1531, finally showing the central axis of the chamber 1506 in a first longitudinal position. 1518 and a constant angle λ. The sheet 1531 is vulcanized on the piston rod 1507 (1532). Angle a between the line connecting the center of axis 1510 to the center of O-ring 1503 and central axis 1518. Flexible impermeable sheet 1531 has an angle γ with central axis 1518 of chamber 1506.

Figure 42B shows details of the suspension of support means 1507, O-ring 1503, and flexible impermeable layer 1531 vulcanized together. Upper layer 1533 includes reinforcements (as in FIGS. 41D-41E), whereas lower layer 1534 does not have reinforcements. Angle β between the line connecting the center of shaft 1510 and the center of O-ring 1503 and central axis 1518.

Figure 42C shows a longitudinal section of the piston 1530 of Figure 42A in a second longitudinal position. Angle II between the flexible impermeable sheet 1531 and the central axis 1518 of the chamber 1506.
19650 Description of the Preferred Embodiment Figure 50 shows a top view of the holder 1224 and the suspension in the holder 1224 of the three rows of stiffeners 1208, 1209, and 1210, respectively, and holes 1240, 1241, and 1242. The small bent ends 1220, 1221, and 1222, respectively, are. Note that the longer the stiffeners 1208, 1209, and 1210, respectively, the longer the small bent ends 1220, 1221, and 1222, respectively, the longer the stiffeners. Hole 1243 in the piston rod (not shown). Center axis 1244. Form 1245 of the piston 1200.

FIG. 51 shows the piston 1200 of FIG. 50, assembled in a pump 1201 with a chamber 1202 and a top 1203, showing a first longitudinal position 1204 of said chamber 1202. Top 1205 is a bearing 1206 in which a piston rod 1207 runs. The bearing 1206 is assembled to said top 1203. The chamber 1202 is of the type whose force is independent of pressure (see 19620). The wall 1207 of said chamber 1202. All the reinforcements 1208, (1209 dashed line) and 1210 have free ends 1211, (1212) and 1213, respectively, of increased diameter. A clamp 1215 closes the piston rod 1207, while at the top 1216 of the piston 1200, a foam is placed on the non-pressurized side 1202'.
12, which can communicate with the fluid in chamber 1202. Stiffeners 1208, (1209), and 1210 have bends 1217, (1218), 1219, and small bent ends 1220, (1221), and 1222, respectively. Said small bent ends 1220, (1221), and 1222, respectively, may be pressed by adjustment member 1223, which is held against piston rod 1207 by O-ring 1227.
The adjustment member 1223 may be rotated within a holder 1224 that is sealed to the impermeable layer 1214. The adjustment member 1223 is rotatable within the holder 1224 and is sealingly connected to the impermeable layer 1214. The piston 1200 is assembled to the piston rod 1207 by the holder 1224 that is mounted within a spring ring 1225 while a clamp 1215 is mounted to a spring ring 1226. A central axis 1243 of the chamber 1202.

52 shows the bend 1218 of the star phena 1209. The increased diameter 1212 of the stiffener 1209. The chamber 1202. The end 1221.
19650-1 Description of the Preferred Embodiment FIG. 55A shows a piston 1300 in a first longitudinal position of an advanced pump, said piston 1300 comprising a foam 1301 having metal reinforcing pins 1302, 1303, 1304 arranged in three circular rows around a piston rod 1306, said foam 1301 being magnetically secured to a magnetic holder plate 1307 of a holder 1308 attached to the piston rod 1306.
13. The foam 1301 is arranged in a direction toward the pressure side of the piston rod 1306 and has an impermeable layer 1305 around the foam 1301. The holder plate 1307 is attached to a holder 1308 by gluing or other means. The holder 1308 can rotate around the piston rod 1306 and has two spring plates 1310 which fit into notches 1312 and 1313 of the piston rod 1306, respectively.
and 1311 are fixed longitudinally to the piston rod 1306. The metal of the pin may be magnetized. The foam 1301 may be made of open cell, preferably PU foam (as discussed in Section 19650 of this patent application), and the open cell vents may be
55B. The holder 1308 has a gland 1317 for an O-ring 1318 sealing said holder 1308 to the piston rod 1306. The central axis 1319 of the piston 1300. The impermeable layer 1305 may be made of natural rubber (NR) and manufactured size and shape of the outside of said piston 1300' when placed in the second longitudinal position of the chamber (not shown). That is, when the piston 1300' travels towards the first longitudinal position, said impermeable layer 1305 expands due to the force of the expanding foam 1301. The reinforcing pins 1302, 1303, 1304 may have a thin layer of PU (not shown) so that the PU foam is better held on said pins 1302, 1303, 1304. This surface treatment can be done, for example, by dipping said pins 1302, 1303, 1304 in a PU foam fluid. The arrow 1335 shows how the foam is squeezed towards the piston rod 1306 as the piston 1300 runs towards a second longitudinal position with a datum 1300'. The low pressure side 1315 of the piston 1300 and the atmosphere 1316.

FIG. 55B shows an enlarged longitudinal section PP of the holder plate 1307. It is attached to the holder 1308. A central axis 1325 of the holder 1308. The holder plate 1307 is made of magnetic material, for example by compressing metal powder and then lining it. At the top of the holder 1308 is a ventilation channel 1314 having a central axis 1321 (see also FIG. 55C) through which the holder plate 1307 (see FIG. 55C) passes and fluid in the open cell is directed toward the piston 1300. between the non-pressurized side 1315 of the air and the atmosphere 1316 near the non-pressurized side 1315. This configuration is also used in the figures. 55E-H (including)
FIG. 55C shows an enlargement of holder plate 1307 on holder 1308. The underside of said holder plate has three rows 1326 of small closed rounded end holes 1329, 1330, 1331 in which the ends of metal pins 1302, 1303, 1304 of FIG. 55A are held, respectively. , 1327, 1328 included. The ends may be rounded so that they fit better into each of the end holes 1329, 1330, 1331. The rounding of the sides of the end hole and the "log" hole means that the radius is slightly larger than the diameter (not shown in this figure) of the pins 1302, 1303 and 1304, respectively, i.e. the pin 1302 , 1303, 1304 to rotate in a plane containing the central axis of the holder 1308. The centers of the rounded end holes are all located in a plane perpendicular to the central axis of the holder 1308. The left side of said end holes 1329, 1330, and 1331 has a respective It is not as deep as the right side of the end hole. Between the holder 1308 and the holder plate 1307 there is a small circular recess 1332 in the holder 1308, which allows the holder to be fixed when the holder plate 1307 is fixed to the holder 1308, for example by screws (not shown). An impermeable layer 1305 can be squeezed between 1308 and holder plate 1307.

FIG. 55D shows an enlargement of protrusion 1333 within the recess 1332 for improved squeezing of impermeable layer 1305 (not shown). This configuration is also used in the embodiment of FIGS. 55E and 55G, which are enlarged in FIGS. 55E and 55G. 55F and 55H respectively.

Fig. 55E shows an alternative solution to that shown in Fig. 55A-D. The new reinforcement and fixation of foam 1351 (not shown) to holder 1359 of piston 1350 (not shown) is shown in detail in Fig. 55F. Said piston 1350 is placed in a first longitudinal position of the advanced pump. The exhaust channel 1314 is identical to that described in Figs. 55B and 55C.

FIG. 55F shows an enlargement of holder plate 1358 and holder 1359. Said piston 1350
includes plastic pins 1352, 1353, and 1354, respectively, as reinforcement of said foam, preferably of the same material as said foam, preferably PU as described in FIG. Rotatably secured at their spherical ends 1355, 1356, and 1357 within the spherical cavities 1360, 1361, and 1362 of the attached holder plate 1358, as discussed above in the description of FIG. 55A. is mounted on the piston rod 1306. Said holder plate 1358 further includes further openings 1363, 1364 and 1365 for guiding said pins 1352, 1353 and 1354, respectively. The pins 1352, 1353, and 1354 may have non-uniform thickness to better hold the foam. The optimized configuration is such that the thickness non-uniformity first causes the pins 1352, 1353, and 1354 to rotate counterclockwise and rotate relative to each other when the piston 1300 is running in the second longitudinal position. When approaching, the spherical ends 1355, 1356, and It may also mean starting a little further away from 1357. See FIGS. 55C and 55D for an illustration of securing impermeable layer 1305 between holder 1359 and holder plate 1358.

FIG. 55G shows an alternative solution to that shown in the figure. Holder 1365 and reinforcement pin 1366
, 55E and 55F with 1367 and 1368.
Figure 56H shows a close-up of said holder 1365, comprising a holder plate 1369 and a circular disk 1370 made of a flexible material. Reinforcement pins 1366, 1367 and 1368 are similar to the pins shown in Figures 56E and 56F, except for pins 1366 and 1367 (and possibly 1368 - also not shown), which each comprise pins 1371, 1372 (and 1373 - not shown), each connected to a spherical end 1355, 1356 (and 1357). Said pins 1372, 1372 are supported by a resilient disk 1370.
When the piston is in the first longitudinal position, the pins 1352, 1353, 1354 are fixed in the first longitudinal position.
will automatically rotate clockwise.
19660 Description of the Preferred Embodiments Figure 60 shows an extended vessel type piston 1400 in a chamber 1401 having a central axis 1402 at the beginning and end of the stroke. The chamber is of a type in which the force applied to the piston rod is approximately constant as the stroke is reduced. The shape of the piston in the second longitudinal position is that of a "starting" elliptical eid 1403 after pressurization from the unstressed production model, which is approximately cylindrical (see Figures 61 and 62). The shape of the piston near the first longitudinal position is an ultimate elliptical 1404 that is approximately a sphere 1405 (dashed line). In between, the piston 1400 has an elliptical shape. The details of the ellipsoid instead of the sphere in the first longitudinal position are the same as the details of the sphere.

FIG. 61 shows a container-type piston 1400 manufactured unstressed and, when stressed, may have an oval or spherical shape. At the bottom of the figure, the immovable cap 1420 has a gland 1421 for an O-ring that is tightened on the piston rod (not shown). Recess 1422 is a gland for an O-ring (not shown) that tightens the bottom of piston 1400 on a bolt (not shown) that locks the bottom of piston rod (not shown) through hole 1432.
The movable cap 1423 at the top of the figure is movable on a piston rod (not shown). A gland 1424 for an O-ring (not shown) clamps the piston at the top of the soud piston 1400.
The caps 1420, 1423 have recesses 1425, 1426 that are used to vulcanize the flexible wall 1427 of the container piston 1400 on the cab 1420, 1423, respectively. This wall 1427 is shown in the figure as having two layers: a reinforcing layer 1428 and a layer serving as a cover 1429 for the reinforcing layer 1428. The dashed lines indicate a possible third layer 1430 and 1431 on top of the other layers 1428 and 1429, respectively, which means that the two layers 1428 and 1429 were vulcanized on the cab 1420 and 1423, respectively. Exists only in position. Central axis 1433. Wall 1427 of piston 1400 is approximately parallel to central axis 1433. Reinforcement stress 1440 is a parallel pattern parallel to central axis 1433. Reinforcement pattern 1441 when there are two layers.

FIG. 61 shows both cabs 1420 and 1423, respectively. On the outside, there are rounded transitions 1434 and 1435 from the flexible wall 1427 to the portion of the wall 1427 that is vulcanized on the cab portions 1425 and 1426 of the cabs 1420 and 1423, respectively. On the inside of the flexible wall 1427, there are rounded transitions 1436 and 1437 just before the flexible wall 1427 meets the cab portions 1425 and 1426 of the cabs 1420 and 1423, respectively. These transitions 1436 and 1437 provide a stable transition of the wall when the pistons are stressed by expansion.
19660-2 Description of the Preferred Embodiments Figure 63 shows the forces from the walls of an actuator piston (not shown) having different cross-sectional areas and different or equal circumferences, and having a central axis 2277, to a wall 2275 of a chamber 2276. A reaction force 2278 (not shown, see Figure 64A) perpendicular to the wall 2275 against the expansion force of the actuator piston wall.
Friction force 2281 from the actuator piston occurs during rolling, specifically when the walls of said actuator piston (not shown, see FIG. 64A) slide over the walls 2275 of the chamber. Reaction force 2279 (not shown, see FIG. 64A) of the walls of the actuator piston on the walls 2275 of the chamber 2276. said component 2280 along the walls 2275 of said chamber 2276. said component 2280 is shown to be larger than friction force 2281. Angle a between the walls 2275 of the chamber 2276 and the central axis 2277 of said chamber 2276.

FIG. 64A shows an oval actuator piston 2285 within a chamber 2286 having:
The wall 2287 of the chamber 2286 has an angle β with the central axis 2288, the longitudinal central axis 2287 drawn at an angle of 20°. A wall 2289 of the actuator piston 2285 is engagedly connected to a wall 2287 of the chamber 2287.

FIG. 64B shows an elliptical actuator piston 2290 in a chamber 2291 having:
The longitudinal central axis 2292 and wall 2293 of said chamber 2291 have an angle γ with the central axis 2292, which is described as 10°. Wall 2295 of said actuator piston 2290 engages and connects to wall 2293 of said chamber 2291. The actuator piston 2290 is shown in three positions 2296, 2297 and 2298 within said chamber 2291, proving that said angles can be used for example in a vehicle motor of the present invention, having a stroke length of 86.4 mm (1595 cc for a Golf Mark II petrol motor) of comparable dimensions to said current petrol motors.
19680-2 Description of the Preferred Embodiments FIG. 80A shows a pump chamber 2101 (but any other chamber configuration may be used) according to section 19620, having a central axis 2102 and a wall 2103 of said chamber 2101 having pistons 2104, 2104' and 2104" according to section 19660, which are expandable, for example, in three different longitudinal positions (first, middle and second, relative), and the wall 2105 of said pistons 2104 includes a separate portion 2106, the cross section of which is in the shape of a circular segment, adapting its position to the inclination a and centerline 2102 of the wall 2103 of said chamber 2101.

FIG. 80B shows details of the enlargement (5:1) of the contact surface 2107 of the wall 2103 of the chamber 2101 and the enlargement (5:1) of the contact surface 2108 of the wall 2105 of the piston 2104, respectively.
The piston 2104 is in a first longitudinal position above which the surface 2108 of the separate wall 2106 can roll and slide. The contact surfaces 2107 and 2108 are respectively hermetically connected to a wall 2103 of the chamber 2101 and a sloped wall 2109 of the piston wall 2105, with the sloped wall 2109 being the closest adjacent wall 2103 of the chamber 2101. Piston wall 21
It has a minimum circumference smaller than 05. Apparently, the surface 2105 of said piston 2104 is transparent from the wall 2103 of the chamber 2101. The contact surface 2107 between the separate wall 2106 and the wall 2103 of the chamber 2101 comprises two surfaces 2110 and 2111, which have an angle b and an angle c, The contact surface 2108 has an angle f of the chamber wall 2103, has a contact angle f with the central axis 2102, and is tightly clamped to the wall 2103 of said chamber 2101. As the circumference of the piston 2104 increases, the separate wall 2106 is tightened towards the wall 2103 of said chamber 2101, while the remaining part of the wall 2105 of said piston 2104 is under tension, thereby causing its It can be pulled back from its original position (FIG. 80F). Lateral centerline 2115 of the piston 2104
. The centerline 2114 of the separate wall 2106 passes through the center 2116 of the point of contact between the separate wall 2106 and the wall 2105 of the piston 2104. Angle d between the lateral centerline 2114 and a line perpendicular to the central axis 2102 of the chamber 2101.

The contact surface 2127 may be simply a portion of a circular segment near the lateral centerline 2114 of the separate wall portion 2106, for example, by vulcanization of a circular portion of a longitudinal cross section of the separate wall portion 2106 with the wall of the piston 2104.

The adjacent wall 2105 is bent more than the wall 2105, which allows a separate wall portion to remain protruding from the wall 2105, thereby providing clearance for the wall 2103 of the chamber 2101 below.

The adjacent walls 2105 of the pistons 2104, 2104', 2104" can also be the case for the separate wall portions 2123 shown in Figs. 84B and 84F, respectively, 80H, and the toroids 2207, 2244. Also, when the piston 2104 is in the first longitudinal position, the circumference of the separate wall portions 2106 is much larger than when the piston is in the second longitudinal position.

FIG. 80C shows the separate wall 2106 when the piston is in the second longitudinal position. Here, the wall 2105 of the piston 2104' is still distinct from the wall 2103 of the chamber 2101, but is smaller than when the piston 2104' is in the first vertical position (FIG. 80B). Angle e between the lateral centerline 2114 and a line perpendicular to the central axis 2102 of said chamber 2101. Lateral centerline 2115 of said piston 2104'.

FIG. 80D shows a separate wall 2106 whose cross section is a circular segment of wall 2105 of piston 2104. When the piston 2104 is in the second longitudinal position, the circumferential position of its wall 2105 is
Enables the piston 2104 to be in that portion of the second longitudinal position of the chamber 2101, with its wall (not shown) 2103 substantially parallel to the central axis 2102 of the chamber 2101.

FIG. 80E shows an alternative spherical separate wall 2112, shown below.
FIGS. 80A-C advantageously provide a separate wall 2112 of the piston 2104" and a wall (not shown) 2103 of the chamber 2101 over the circular segment shape of the separate walls 2106 of FIGS. 80A-C. There can be a relatively large clearance between the lateral centerline 2117 of the separate wall 2112.

FIG. 80F shows an alternative half-rond shape of a separate wall portion 2113 having a centerline 2114, which is identical to the lateral centerline 2115 of the piston as shown in the figure. 80A-C When the piston 2104″ is in an as-manufactured second longitudinal position, the separate wall portion is vulcanized onto the piston according to section 19660 (enlarged).

Figure 80G shows an improved version of the embodiment of Figure 80F, where the lateral centerline 2120 of the separate wall portion 2113 is located below a line 2121 through the longitudinal midpoint of the flexible wall of said piston 2104, ensuring a suitable contact area with the conical chamber at the second longitudinal position, i.e., the portion closest to the second longitudinal position of said piston 2104. Other chamber configurations can provide alternative positioning of said separate wall portion 2113 and its lateral centerline 2120.

FIG. 80H shows a longer piston 2126 (than shown in FIG. 80G) in a first longitudinal position in which the piston 2126 is expanded. The centerline 2122 of the separate wall 2123 is connected to a chamber (not shown).
The piston 2126 is located below the lateral centerline 2124 through the longitudinal midpoint of the flexible wall 2125 to ensure an adequate contact area with the piston 2126. Other chamber configurations may provide other positioning of the separate wall 2106 on the wall 2125 of the piston 2126.

80I and 80J show a piston 2130 having a reduced circumference at its lateral centerline 2131 as produced (and thus in a second longitudinal position). The centerline 2132 of the separate wall portion 2133 remains as manufactured. This prevents contact between walls 2134 of the chamber 2136 and other portions of the walls 2134 of the chamber 2136 when the walls 2134 of the chamber 2136 are varied parallel to the central axis 2138 of the chamber 2136. , particularly when moving from a second longitudinal position 2137 outside the chamber in the direction of a first longitudinal position 2139, as shown in FIG.
(according to the authors), any other chamber configuration may be used), allowing for better avoidance. A longitudinal centerline 2135 of the piston 2130.

FIG. 81A shows a pump chamber 2101 according to section 19620 having a central axis 2102 (but any other chamber configuration may be used) and a wall 2103 of said chamber 2101, which may be expandable in three different longitudinal positions 2140, 2140', 2140", e.g., having an expansion piston 2140 according to section 19660 according to FIG. 61, the wall 2141 of said piston 2140 having more than one, e.g., two separate wall portions 2142 and 2143, the respective longitudinal cross sections of which are circular for each of the walls 2103 of said chamber 2101 in the following ways: parallel (at the extreme second longitudinal position), concave (at the transition from the extreme second longitudinal position to a position close to the first longitudinal position), and convex (from the transition to the first longitudinal position).

81B shows the scaled-up contact surfaces 2144/2145 and 2146/2147 of the individual walls 2142 and 2143, which are sealingly connected to the wall 2103 of the chamber 2101 at a first longitudinal position and to the inclined portions 2148 and 2149 of said piston wall 2141, respectively, said inclined portions 2148 and 2149 having a smaller minimum perimeter than the adjacent piston wall located closest to the wall 2103 of said chamber 2101. The separate walls 2142 and 2143 are positioned at a distance g from each other to avoid the wall 2141 of said piston 2140 engaging and/or sealingly engaging with the wall 2103 of said chamber 2101. Depending on the inclination of the walls e 2103 of the chamber 2101, there is a separate wall 2143 located closest to a first longitudinal position closer to the lateral centerline 2130 of said piston 2141, and a separate wall 2142 closest to a second longitudinal position. In order to avoid the pistons 2140, 2140' rolling on the surface 2103 of the chamber 2101, the position of the pistons 2140, 2140' may be different from the above mentioned, depending on the shape of the pistons 2140, 2140' and the inclination of the walls 2103 of the chamber 2101, with the aim of the pistons 2140, 2140' avoiding continuously curved walls.

81C shows an enlarged detail of the contact surface when the piston 2121 is positioned between a first longitudinal position and a second longitudinal position, and here there is no contact between the wall 2136 of the piston 2140' and the wall 2103 of the chamber 2101.

With the inclined walls 2103 of the chamber 2101, the angle between the chamber wall 2103 and a line perpendicular to the central axes 2137 and 2138 of the separate parts is not the same and is greater than the angle in FIG. 81B. Please note.

FIG. 81D shows the piston as manufactured (enlarged to 12.5:1), which is in an extreme second longitudinal position. Separate walls 2142 and 21 as in Figure 80D
A piston 2140'' containing 43 is located within said chamber 2101 (not shown), where its wall 2103 (not shown) is parallel to the central axis 2102 of said chamber 2101 (not shown). The arrow indicates the lateral centerline 2130 of the piston 2140''.

Figure 82A shows a chamber 2101 of a pump according to section 19620, having a longitudinal centerline 2102, and having an inflatable piston 2145, said pistons 2145, 2145', 2145'' each having three different longitudinal Shown in a directional position, said piston wall 2146 comprises two parts 2147 and 2148, each having a different circumference in a cross-section, with the part 2147 closest to said first longitudinal position having the largest circumference. and includes contact areas 2149, 2149', and 2149'' between the wall 2103 of the chamber 2101 and the piston wall 2146, respectively. The size of the contact area can be different in each of the three longitudinal positions.

FIG. 82B shows an enlarged (5:1) detail of the contact area 2149 when the piston 2145 is in a first longitudinal position. Two piston walls 2147 and 2148. The piston wall portion 2147 is
a skin 2150 terminating directly below the contact area 2149 and a stepped transition 2199 from wall 2147 to wall 2148 of wall 2146, the piston wall 2147 being the closest to the first longitudinal position of the piston. Wall portion 2147 is closest to wall portion 2103 of wall portion 2101 of wall portion 2148 closest to the second longitudinal position. Beneath said skin part 2150 there may be another skin part 2151, preferably a layer, optionally a reinforcing layer. This skin portion 2151 is preferably present on the entire piston wall 2146. Where the outer skin 2150 of the piston wall 2147 ends, an inner skin 2152 begins (preferably an overlap), which is part of the piston wall 2148 and located behind the outer skin 2151. 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 lateral centerline 2153 of said piston 2145 is closer to a first longitudinal position than the stepped transition 2199 of wall 2146 from wall 2147 to wall 2148.

FIG. 82C shows an enlarged detail of the contact area 2149 when the piston 2145 is positioned between a first longitudinal position and a second longitudinal position. Also, here there is no contact between the skin 2151 of the wall 2148' of the piston 2145' and the wall 2103 of the chamber 2101. As shown, the contact area 2149' of the wall 2147' of the chamber 2101 wall 2103 may be different from the contact area 2149 of FIG. 82B. is the lateral centerline 2153' of the piston 2145'. This centerline 2153' may be positioned closer to the first longitudinal position of the step transition 2199 of the wall 2146 from the wall 2147 to the wall 2148.

FIG. 82D shows piston 2145″ with wall 2146″ (magnified 12.5:1) of said piston 2145 in a second vertical position, no chamber is shown. Wall 2147 has diameter φz and wall 2148 has diameter φz-z1 (z1>0). Transverse centerline 2153″ of piston 2145″
FIG. 83A shows the piston 2121'' (inclusive) and piston rod 2151 of FIGS. 82A-82D produced in a second longitudinal position.

FIG. 83B shows the piston 2121 of FIG. 83A in a first longitudinal position, where the piston 2121 is expanded at arrow 2152 via its piston rod 2151.
FIG. 83C shows the piston 2121 of FIG. 83B in a first longitudinal position (arrow 2153) in which the piston 2121 is retracted after the position of the movable cab 2154 is fixed on the piston rod 2151 by the clamp 2155. Shown through 2151.

Figure 83D shows the enclosed space (2159) of its piston rod 2151 with foam (not shown) (2158).
FIG. 83C shows the piston 2121 of FIG. 83C in a first longitudinal position through which a cavity (not shown) (2156) of the piston 2121 of FIG. 83C is filled. The foam may be a PU foam (polyurethane), preferably as a mixture of a memory PU foam type (see section 19640 of this patent application) and a standard PU foam type. This is a well compressible foam with an open cell structure.

FIG. 83E shows the piston 2121 of FIG. 83D in a first longitudinal position, after the clamp 2155 is removed, the cavity (not shown) (2156) of the piston 2121 is exposed to the foam (not shown). (2158) is filled. Here, it is possible to compress the wall 2146 of the piston 2121, for example by moving the piston rod 2151 to include it. Said piston 2121 does not require significant force from the first longitudinal position to the second longitudinal position.

To achieve a suitable sealing force and/or a suitable compression force on the piston,
Through the open cells of the foam it is necessary to add a compressed fluid, such as a gaseous medium.

FIG. 83F shows the piston 2121″ with the inserted and compressed foam (not shown) (2158) of FIG. 83D and its piston rod 2151 in combination with a pressure sensor 2160 and an expansion valve 2161 according to FIG. 3B of WO 2109/083274 for the sealed space (2159) (not shown) + cavity (2156) (not shown) of the piston 2121. The piston rod 2151 is preferably of the type whose sealed space (not shown) (2159) has a constant volume (WO 2110/094317), optionally with a variable volume according to WO 2100/070227.

Figure 83G shows an enlargement of the combined sensor-expansion valve configuration of Figure 83F. Expansion valve 2161 with inlet 2196 for closed space 2159 of piston rod 2151. Pressure sensor 2160 according to WO2111/000578
Entrance 2194 and its exit 2195.

FIG. 83H shows the inserted foam (not shown) (2158) of FIG. 83D and its piston rod 2151, as well as the enclosed space (2159) (not shown) of said piston 2121 + cavity (2156) (not shown).
FIG. 5 of WO 2111/000578 for a piston 2121″ with a combined pressure sensor 2162 and an expansion valve 2161 according to FIG. 5 of WO 2111/000578 for a piston rod 2151. The piston rod 2151 is preferably of the type whose enclosed space (not shown) (2159) has a constant volume (WO 2110/094317) or optionally has a variable volume according to WO 2100/070227.

FIG. 83I shows a close-up of the combined sensor-expansion valve configuration of FIG. 83H. Expansion valve 2161 with inlet 2196 for sealed space 2159 of piston rod 2151. Pressure sensor 2162 according to WO2111/000578.
and its entrance 2194 and exit 2197.

FIG. 83J illustrates the inserted foam (not shown) (2158) of FIG. 83D and its piston rod 2151, as well as the enclosed space (2163) (not shown) of said piston 2121 + cavity (2156) (not shown).
9 of WO 2111/000578 for a piston 2121″ having a combined pressure sensor 2164 and an expansion valve 2165 according to FIG. 9 of WO 2111/000578 for a piston rod 2151. The piston rod 2151 is preferably of the type whose enclosed space (not shown) (2163) has a constant volume (WO 2110/094317) or optionally has a variable volume according to WO 2100/070227.

Figure 83K shows an enlargement of the combined sensor-expansion valve configuration of Figure 83J. Expansion valve 2165 with inlet 2198 for closed space 2163 of piston rod 2151. Pressure sensor 2164 according to WO2111/000578
Entrance 2194 and its exit 2199.

The expansion of the PU foam to its default size as shown in FIG. 83D is performed by the piston 2121
The force for the expansion is provided by a spring 2166 which pulls the movable cab 2154 towards a fixed cab 2167 to blow up the wall 2146 of the piston rod 2151. The spring 2166 is positioned on the piston rod 2151 and attached to the movable cab 2154 and a fixture 2168 which is positioned within the structure 2168 of the piston rod 2151.

To solve the problem that the volume of the expanded ellipsoid is much larger than the volume of a small enclosed space, such as a piston rod, the expanded volume is substantially reduced, for example to the volume of the expandable troy, while the expansion of the piston walls remains. This means that when pushing the expanded piston from a first longitudinal position to a second longitudinal position, the internal pressure rise is smaller, and the piston can be reduced in size (without clogging).

FIG. 84A shows a piston 2170 of oval type in a first longitudinal position (not shown) with a central axis 2171, and a piston rod 2172, a fixed cab 2173, and a movable cab 2174, on which Both elastically flexible walls 2175 of the piston 2170 are attached, for example by vulcanization, said walls 2175 having a reinforcing layer 2176. The piston 2170 has walls of the type shown and described. 82A-D (including) said wall 2175 is used inside a vault 2177 in which an inflatable toroid 2178 is placed, which has a wall 2179 with reinforcement 2180 so that said toroid 2178 The circumferential size is increased by a higher internal pressure and decreased by a lower pressure, without a change in its outer cross-sectional diameter d. This means that when the piston 2170 is in a second longitudinal position of a chamber (not shown), the wall 2175' of the piston 2170 is approximately parallel to the central axis 2171 and the toroid 2178' is It is meant to be placed adjacent to the piston rod 2172 with the wall 2175 and the aperture 2181 in order to give space to the toroid 2178'. The wall 2179 of the annular body 2178 is much more telop than when the piston 2170 is in the first logical position with the reinforcement 2180 having an angle greater than 54° 44'. The flexible hose 2182 communicates with the closed space 2183 of the piston rod 2172 through its channel 2190, and the other end of the channel 2182 communicates with a channel 2184 in the annular body 2178. The U-shaped vault 2177 has the pistons in the first and second
The toroid 2178 is guided as it moves between vertical positions. To reduce the force required for expansion of the wall 2175 of the piston 2170, a tension spring 2185 is applied to the piston rod 2172 when the piston 2170 moves from the second longitudinal position to the first longitudinal position.
and is attached to the movable cab 2174 and a hook 2186 fixed to the tightening position 2181 of the piston rod 2172. Observe the small diameter of the channel 2184' within the annulus 2178' when the piston 2170 is in the second longitudinal position of the chamber. Cross section of flexible hose 2182 with channel 2190. Said channel 2190 is at one end communicating with enclosed space 2183 and at the other end communicating with channels 2184 and 2184'. The high-pressure side 2187 of the wall 2175 of the piston 2170 is a foam 2193 (e.g., PU foam of the type disclosed in section 19630 of this patent application) within the interior 2192 of the walls 2175-2187 of the piston 2170; supported by ). Since the foam 2193 has open cells,
It communicates with an enclosed space 2183 (not shown), or preferably with a low pressure side 2188 (not shown or see FIG. 84B), optionally with a high pressure side 2191 of said piston (not shown). The annulus 2178, 2178' is shown to have a central axis 2194 that converges with the lateral central axis 2195 of the piston 2170 to obtain an optimal ellipsoid shaped wall 2175. The high pressure end of the piston rod 2172 is shown with a pressure sensor illustrated in the figure. 83H/I.
FIG. 84B shows an ellipsoidal type piston 2200, which is an improved and simplified version of the piston 2170 of FIG. 84A, where the entire interior 2201 within the wall 2202 of the piston 2200 is 84A, including the PU foam 2203. Inside the wall 2202 of the piston 2200 is a channel 2205 that is attached (eg, by vulcanization) to the inside of 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 within the piston rod 2209 at the other end. The form 2203 is in communication with an enclosed space 2208 via a channel (not shown) or preferably with a low pressure side 2210 of said piston 2200 via a channel 2211 in a movable cab 2212. or optionally in communication with a high pressure side 2211 (not shown) of the piston 2200. The annular body 2207 is aligned with the lateral central axis 22 of the piston 2200 in order to obtain an optimal oval wall 2202.
It is shown to have a central axis 2213 that converges with 14. However, as disclosed in fig. Due to the shape of the chamber, the contact surfaces 2107, 2108 of said separate part 2106 with a central axis 2114 are more closely aligned than the lateral central axis 2115 of said piston 2104, 2104', 2104'' in the second longitudinal direction of the chamber. 2114, 2115 do not converge with each other. This also means that, along with the contact area of the annular body 2207 with the wall of the chamber (not shown), it also This may be the case as it may be located at a lower position than the central lateral axis 2214 of the piston 2200 (not shown).The high pressure end of the piston rod 2209 is shown with the pressure sensor described in the figures. 83H/I.
FIG. 84C shows a piston 2220 having the same structure as piston 2170 of FIG. 84A. However, the wall 2221 on the low pressure side of the piston 2220 is excluded. The wall 2221 is not part of an ellipsoid as shown in FIG. 84A, but is part of a cone shown in tension.

FIG. 84D shows spherical piston 2230 in a first longitudinal position, 2230" in a second longitudinal position, having a central longitudinal axis 2231 and a central transverse axis 2232, 2232". The pistons 2230", 2230 include separate portions 2231", 2231" having transverse central axes 2233, 2233, respectively. The transverse central axes 2233, 2233" are positioned below the transverse central axes 2232, 2232", the first mentioned being positioned closest to the second longitudinal position. Other configurations of the separate parts shown in FIGS. 80A-E are also possible.

FIG. 84E shows the first
A spherical piston 2235 in a longitudinal position and 2235'' in a second longitudinal position. Stepped transition 2238 of wall 2234 from wall 2239 to wall 2240.

FIG. 84F shows a spherical piston 2241 in a first longitudinal position and 2241″ in a second longitudinal position, having a central longitudinal axis 2241 and a central transverse axis 2243, 2243, respectively. Said piston 2241 includes separate portions 2244, 2244″ having respective transverse centerlines 2245, 2245″, the last mentioned being aligned with the central transverse axis 2243 of said pistons 2241, 2241″, respectively.
, 2243" and is therefore closest to the second longitudinal position. Expansion of the toroid 2244 may be performed as shown in FIG. 84A or 84B.
19690-2 Pistons and chambers, gearboxes
Rotating piston Fig. 90AB shows a piston rotating in a chamber, which may be fixed, but which can always counteract the torque obtained by the piston. The closed space (channel) may be part of an axis, the center of which may be around which the piston rotates, for example similar to a piston moving on a crankshaft. Figs. 11A (CT4), 11G (ESVT2), 11I (ESVT5). 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 arranged perpendicular to the axis of the axle. The connecting rod between the piston and the axle may comprise a closed space of the piston, which may communicate with the space in the piston and with the closed space in the axle. For example, if a spherical piston is used, the extension rod connecting the sphere to the channel in the axle may be constructed similarly to the rod shown in Figs. 14F and 14G, the length of the connecting rod is such that it can always adapt to the current distance between the center of the piston and the center of the axle (Figs. 90C,D). It depends on how the connecting rod is connected to the shaft which pressure management technique can be used, i.e. CT and/or ESVT, or a third type. CT requires a valve function, i.e. a continuous open and closed connection between the channel of the connecting rod and the channel of the shaft. ESVT requires an open connection between the channels.

The possibilities of configuring the joint between the connecting rod and the axle additionally depend on how the torque is transmitted from the piston through the connecting rod to the axle when the chamber can be fixed. Transmitting torque from the piston to the rotating shaft via the connecting rod means that there is a fixed connection between said two components. If an ESVT pressure management system is desired, the structure of the joint is relatively simple, comprising a fixture (e.g. teeth (connecting rod) + corresponding groove (axle)) and a channel through the fixture; Channels (Figure) in constant communication with channels in the connecting rod and axle. If a CT pressure management system is desired, the structure of the joint may be more complex. This may include a serial land/or parallel solution of the fixture and rotating channel, the opening of which contacts the opening of the fixed channel during part of the rotation. Serial solutions contain constructs.

Since the fixture and the rotation are located at at least two different positions on the axis, at least two joint parallel solutions comprise a structure in which the fixture and the rotation are combined into one joint. .

To increase the torque, several pistons may be operating in one chamber, and there may be sub-chambers in said chamber, for example, if there is one piston per sub-chamber, each piston may preferably be located at the same circular position in each sub-chamber. This can be done to simplify the construction, so that the sealed space of each connecting rod per piston communicates with the sealed space of the shaft. The pressure in each piston is the same as the pressure in the channel in the other piston.

Another possibility is that one or more piston-chamber combinations are combined with an X cylinder motor (x>1) in which one or more pistons are/are rotating in a chamber, and said combinations can rotate the same central axis (FIG. 92A), allowing the torque of each piston to be transmitted to carry out the purpose of the motor.
Rotating Chamber Figure 91A shows a chamber rotating around a piston, which may be fixed but always able to counteract the torque available 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 arranged perpendicular to the axis of the axle. The enclosed space (channel) may be part of an axis around which the chamber rotates, such as a chamber. figure. 13A, (CT6); 12D, 13E, F, G (ESVT); 14E (ESVT7).

The connecting rod between the piston and the axle may include a sealed space, which communicates the space within the piston with the sealed space within the axle (FIGS. 91A, B). ).

For example, if a spherical piston is used, the connecting rod connecting the sphere to the channel of the axle may be constructed similarly to the rod shown in the figures. The length of the connecting rods 14F and 14G (FIGS. 90C, D) so that they can always accommodate the current distance between the center of the piston and the center of the shaft. This structure is the same as that of a moving piston combination.

What has been said in the previous chapter about the structure of the connecting rod/axle junction when the piston is moving also applies to the situation when the chamber is moving.
In the situation where the chamber is moving, two main groups of solutions are possible: one is when the axle is fixed and the chamber rotates around said axis and said chamber transmits the torque (Fig. 92A), the other group is when the axle is rotating and may transmit the torque induced by the chamber (Fig. 92B,C; Fig. 93A,B).

If the axle is rotating the connecting rod (FIG. 91AB), ESVT may be used or CT may be used (FIG. 91E). This depends on the possibility of forming a valve between the closed space of the connecting rod and the closed space of the axle. For example, two valves enable CT (Figure 91C,D) and one valve does not use ESVT (Figure 91E).

To increase the torque, there may be multiple pistons within one chamber and subchambers within said chamber, and if there is one piston per subchamber, each piston may be located at the same circular location within each subchamber, or may be located at different circular locations, for example. figure. 13A-G, 14A-H. Positioning in the same circular position may be performed to simplify the construction, so that the enclosed space of each connecting rod per piston communicates with the enclosed space of the shaft. The pressure in each piston is the same as the pressure in the other pistons.

Several solutions can be combined for all parameters when the chamber is rotating.
The chamber rotates, for example, around a bearing mounted on an axle on the chassis of a vehicle, and the axle rotates, for example, around a bearing mounted on the chassis while the piston is fixed to said chassis. When rotating, for example in the same direction, the connecting rod may be fixed between the fixed piston and the fixed axle. The axle and the chamber may further rotate in opposite directions. The connecting rod and axial channel of this combination of solutions are preferably in communication with the ESVT system (FIGS. 10M, 13C).

If the chamber rotates around a bearing mounted, for example, on the chassis of a vehicle, and the axle is fixed, for example, on said chassis, the piston moves against said axle in order to obtain the force moment necessary to rotate said chamber. It can be fixed by a connecting rod fixedly attached to the Said connecting rod and axial channel of this combination of solutions may preferably be in communication with the ESVT system (Figures 91A-C). figure. 91 G-I shows a similar solution in which the bearing of the chamber is mounted on the axle.

When there are multiple piston-chamber combinations, where the chambers contain one or more pistons, the chambers of the combination can transmit torque through a housing containing at least one chamber, and the housing can transmit the torque, for example, to a bare box or automatic gear (e.g., Variomatic(R)), to wheels, a propeller, etc.

Moreover, each chamber of the combination is capable of transmitting its torque to the shaft on which it operates (FIG. 93A, B), which rotates around a fixed axle, the sealed space of the fixed piston in the connecting rod communicating with a pressure management system, preferably an ESVT system, through a channel in the fixed axle.
19690-2 - Description of the Preferred Embodiments Fig. 90A shows one rotating piston 4000 located adjacent to a first longitudinal position in a circular chamber 4001, the piston 4000 being connected to an axis 4002 by a connecting rod 4003, said axis 4002 and said connecting rod 4003 each comprising one each of channels 4004 and 4005 communicating with each other. Said channel 4005 is a (first) closed space of the piston 4000. Said channel 4004 is a (second) enclosed space of said piston 4000. Said channel 4005 is a (second) enclosed space of said piston 4000.
The piston 4000 communicates with a space within the wall of the piston 4000. The central axes 3997 and 3998 are horizontal and vertical, respectively. The central axis of the chamber 4001 is centered 3995 of said axes 3997 and 3998. The axis of said axis 4002 (not shown as such) preferably passes through said center point 3995 and is preferably disposed perpendicular to a plane passing through the central axis 3996 of said circular chamber 4001. The central axis 4008 of the connecting rod 4003 preferably passes through said center point 3995. The piston 4000' is shown in a final first circular position of said chamber 4001 and a second circular position of the piston 4000". The circular chamber 4001 is configured over 360 degrees from the second longitudinal position to the first longitudinal position. The piston 4000 "rotates around the center point 3995 clockwise within said chamber 4001". The channel 4004 is in communication with a pressure management system, which may be a CT and/or ESVT system. A counterweight 3994 is located on the opposite side of the connecting rod 4003 relative to the center point 3995.

Figure 90B shows the details of the assembly of the connecting rod 4003 to the shaft 4002. This is done by having a hub 4009 on the shaft 4002 slidably mounted on the shaft 4002 in the longitudinal direction of the shaft 4002, with the teeth 4007 of the shaft 4002 fitting into corresponding grooves 4007' of said hub 4009. This construction allows torque to be transmitted from the connecting rod.

4003 to the axle 4002. This configuration also allows for some communication between the channel 4006 in the axle and the channel 4006' in the wall of the hub 4009 and the channel (first sealed space) 4005 in the connecting rod 4003 and the channel (second sealed space).

4004 in said shaft 4002. A central axis 4008 is the central axis of the channels 4005, 4006 and 4006' respectively and is also the central longitudinal axis of said connecting rod (4003). This central axis 4008 is positioned perpendicular to the central axis of the shaft 4002 (not shown). The connecting rod 4003 is attached to said hub 4009. The connecting rod 4003 is shown as having a central rod 4010 in which the sealed space 4005 is located and a reinforcing fin 4011 between which a bolt 4016 is located for attaching the connecting rod 4003 to said hub 4009. A washer 4012 and a spring washer 4013. An end 4017 of said central rod 4010 is placed in a recess 4015 of said hub 4009. A sealing 4018 between said end 4017 and said recess 4015. A counterweight 3994 is shown as part of the hub 4009 .

FIG. 90C shows the extension rod 4020 of the connecting rod 4003 to which the piston 4000 is attached. The piston 4000 is shown to be located near a first circular position 4021. The rest is of the same structure as shown in FIG. 14F. The connecting rod 4003 comprises an extension rod 4020 moving with a sealing sliding fit between the axis 4002 and the axis 4002 by two O-rings 4021 and 4022 in the end 4023 of the channel 4005 of the connecting rod 4003 so as to allow compensation for the changing distance of the wall 4024 of the piston 4000 to said axis 4002. In said extension rod 4020 there is a channel 4025 that communicates with the space 4026 of said piston 4000 and the channel 4005 of the connecting rod 4003 via a channel 4027. The distance 1 between the end 3991 of the extension rod 4020 and the intersection 3990 ′ of the central axis 3996 of the chamber 4001 and the central axis 4008 of the connecting rod 4003 .

FIG. 90D shows the extension rod 4020 of the connecting rod 4003 with the piston 4000" attached, when the piston 4000 is in the second circular position 4028. The rest is as shown in FIGS. 14G and 90C. Identical structure. Distance 1' between the end 3991 of the extension rod 4020 and the intersection of the central axis 3996 of the chamber 4001 and the central axis 4008 of the connecting rod 4003. Length 1'< 1 (Fig. 90C).

FIG. 90E shows the configuration of FIG. 90A in communication with the CT-pressure management system according to FIG. The joint 4051 between the connecting rod 4003 and the shaft 4002 in Figures 90A,B is according to Figure 11D. Connecting rod 4002 channel 4005, axle 4002 channel 4004
It communicates with The last mentioned channel 4004 is in communication with channels 822 and 823. For further explanation of reference numbers in the above drawings, please refer to FIGS. 11A and 11D.

FIG. 90F shows an ESVT (pressure management system) according to FIG. 11G and a joint 4052 according to FIG. 11T for the transition of the axle 4002, including the channel 4004, with the channel 4005 of the connecting rod 4002 of FIGS. 90A,B. See Figures 11G and 11T for further explanation of the reference numbers in the drawings.

FIG. 90G shows an ESVT (pressure management system) according to FIG. 11I and a joint 4052 of an axle 4002 according to FIG. 11T, with a channel 4004 and a connecting rod 4003 constituting a channel 4005 as shown in FIG. 11I. 90A,B. For further reference numbers of the above figures, please refer to FIGS. 11I and 11T.

FIG. 90H shows an ESVT-pressure management system based on FIG. 90G with the combination of a camshaft 4060 controlling the timing of the ESVT system of FIG. 11I according to FIG. 11Q, while energy is obtained from a combustion motor 4061 derived from the electrolysis of H2O, driven by H2. For further explanation of the reference numbers of the above figures, and other details, please refer to FIGS. 90G, 11I, 11T, and 11Q.

Diagram 901 shows four rotating pistons 5070, 5071, 5072, 5073resp. Said circular chambers 5074 may preferably be fixed within a circular chamber 5074 comprising four sub-chambers 5075, 5076, 5077, 5078, one for each piston. The rotating pistons 5070, 5071, 5072, 5073 are each arranged at the same circular position in each of the subchambers 5074, 5075, 5076, 5077. The circulation of the piston is shown to be clockwise around the center point 5079 of the circular chamber 5074. Each piston 5070, 5071, 5072, 5073 rotates around the same axis 5085, and its center is the same as the center point 5079. Each piston piston 5070, 5071, 5072, 5073 is connected to said shaft 5085 by a connecting rod 5080, 5081, 5082, 5083 comprising an extension rod 5090, 5091, 5092, 5093 as shown in Figures 90C,D. be done. In fact, this structure for said pistons 5070, 5071, 5072, 5073, connecting rods 5080, 5081, 5082, 5083 and extension rods 5090, 5091, 5092, 5093 is four times as large as the structure shown in the figures. 90A,B. The four connecting rods 5090, 5091, 5092, 5093 are all assembled to a common hub 4029 by bolts. The hub 4029 is fixedly attached to the axle 5085 by teeth (4007) on the axle 5085 so as to fit into corresponding grooves (4007') in the hub 4029, as shown.

90J shows an enlarged view of the assembly of connecting rods 5080, 5081, 5082, 5083 and shaft 5085 of FIG. 901. In fact, this joint is four times the joint shown in FIG. 90B with four equal circle segments across 360. The 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 said shaft 5085 and thus with each other. This configuration preferably allows for direct communication between the space within each piston 5070, 5071, 5072, 5073 (see Figures 90C,D) and the channel 5090 within the shaft 5085. Works with management systems.

Figure 90K shows the configuration of Figure 901, J communicating with a.
Further development of doubling: a new joint 4054 mirrored around the central axis of said axle of joint 4052 based on FIG. 11T in combination with the ESVT pressure management system as shown in FIG. 11I and the common hub 4053 of FIG. 90J. See Figure 11T for a description of this portion of the fitting.

Figure 90L shows a preferred embodiment of a motor based on the structure of the joint 4054 shown in Figure 90K in combination with a camshaft 4060 that controls the timing of the ESVT system, while energy is derived from electricity from a battery 832 according to Figure 11Q. Energy is obtained from the combustion motor 4061, driven by H2. See Figure 90K for further reference numeral descriptions of the drawings.
and 11 Q.

FIG. 91A shows one circular chamber 4030 (over 360°), which rotates counterclockwise around an axis 4032 and is suspended by three spokes 4034. Said spokes 4034 are shown in a cross section different from that of the connecting rod 4033. A piston 4031 is placed near a first circular position in said circular chamber 4030. Said piston 4031 is preferably fixed by the connecting rod 4033 and the last-mentioned suspension hub 4038 is fixed on said axle 4032 by means of teeth and corresponding grooves (see FIG. 91B) that receive a reaction force from the circular chamber 4030 on the piston 4031. Between the hub 4035 of said spokes 4034 and said axle 4032 a bearing 4039 is provided, which is fixed to the hub 4035 of said spokes 4034 by a suitable fit and allows the hub 4035 of said spokes 4034 to rotate said axle 4032. Belt 874 is
It rotates near the edge of the chamber housing 4036 and moves along the direction of rotation of the chamber 4030 .

FIG. 91B shows the assembly of the connecting rod 4033 and the axle 4032 in detail. The hub 4035 of the spokes 4034 is provided with a bearing 4039 with a suitable fit which rotates together with the rotating hub 4035 of the spokes 4034. The bearing 4039 belongs to a different cross section than the one including the channels 4044 and 4045 in the wall of the axle 4032 and in the wall of the top 4038-1 of the hub 4038, so no valve function is arranged here. The hub 4038 of the connecting rod 4033 is made up of two parts, an upper part 4038-1 and a lower part 4038-2 which are connected to the connecting rod 4033. The said top and bottom parts are connected to the hub 4038 in addition to the connecting rod 4033.
4038-1 are bolted together by bolt 4040 which bolts to hub 4038-2. Spring washer 4041 and washer 4042. Hub 4038 has a groove 4007' which fits into hub 4038-1. There is some communication between channel 4043 in said axle 4032, channel 4044 in the wall of axle 4032, channel 4045 through the top wall of hub 4038-1 and channel 4046 through connecting rod 4034. The channel through the extension rod is not shown.
- See Fig. 90C, D. For constant communication, the use of an ESVT system is preferred, especially in applications with multiple chambers on one axle, the use of a CT system is optional.

All solutions for combining with CT and/or ESVT pressure management according to the embodiments of Figures 90A-90D are also applicable to the embodiment of Figures 91A,B.
Based on the configuration shown in Figures 91A, B and similar figures, a chamber having four subchambers with four pistons is not shown, but is only mentioned here. 901, the chambers rotate around an axis whose central axis passes through the center point of the centerline of the circular chamber. The space in each piston is always in communication with the channel in the axle through the channels (closed spaces) of each of the four extension rods and connecting rods, and this configuration preferably functions in an ESVT system.

Figure 91C shows a structure equivalent to Figure 91B, with the difference that the bearing 5100 is part of the hub 5101 that assembles the connecting rod 5102 to the axle 5103, and that the spokes 5105 are connected to its hub 5106 (Figure 9 (see) both the axle 5103 and the connecting hub 5104. Also, a channel 5109 in the wall of the shaft 5103 is positioned in the portion of the shaft 5103 where the bearing 5100 is located.

Section KL is a section through connecting rod 5102 and hub 5101 of shaft 5103, where shaft 5103 is fixedly connected to hub 5104 by teeth 5107 that fit into grooves 5108. Section NM is a section through hub 5106 of spokes 5105 (see FIG. 91D) and hub 5106 of shaft 5103, where hub 5106 can reverse said shaft 5103 by means of bearings 5100.

Figure 91D shows cross sections N-M and K-L of Figure 90C. Further, a cross section of a chamber 5110 is shown, the wall 5111 of said chamber 5110 comprising an opening 5112 for an extension rod (not shown, see Figures 90C,D) and a larger opening 5113 for a connecting rod 5102.

The fit between the bearing 5100 and the hub 5101 of the connecting rod 5102 is such that the bearing 5100 cannot pivot within the hub 5106 of the spokes 5105, but can pivot within the hub 5100 of the connecting rod 5102. The fit between the bearing 5100 and the bearing 5103 is such that the bearing can orbit the bearing 5102. As a result, when chamber 5110 is rotating about the axle 5103, chamber 5109 does not have constant communication with the channel 5114 of the axle 5103. Here, a CT pressure management system can be used.

With the embodiment shown in the figure. 91A-D (inclusive) are preferred embodiments of the remaining embodiments of the motor previously shown in FIG. 90E (CT). 90F-H (including ESVT)
FIG. 91E shows a connection between channel 4035 of the connecting rod and channel 4034 of axle 4032, allowing for some communication between the channels 4035 and 4034. Bearing 4039 is rotating with connecting rod 4033 at the same rotational speed, so channel 4037 is always in communication with channel 4035 of connecting rod 4033. Central axis 4036 of connecting rod 4033. Axle 4040 includes an additional channel 4041. The channel 4041 is in constant communication with the channel 4032 of the axle 4040 via channel 4042. Said channel 4041 is also in constant communication with channel 4037 of bearing 4039 via channel 4045 of upper hub 4038-1. Part 4046 of axle 4040 has a reduced diameter approximately around the channel 4042 in the wall of said part 4046. Channel 4035 of connecting rod 4035 is in constant communication with piston 4031 according to the figure. 90C, 90D (when using spherical pistons) A channel 4034 in the axle 4032 communicates with the pressure management system.

ESVT8 may be working fine with this configuration.
For valves used at the axle-to-conrod junction, see Figure 11D when using CT2. See FIG. 11D, as shown in FIG. 90E (Reference 4051). For ESVT1, see Figure 11T and then, for example, Figure 90F (reference number 4052) and Figure 90K (
Reference number 4054).

The fit between the bearing 4039 and the upper hub 4038-1 and the lower hub 4038-2 may be such that the bearing cannot move relative to the hub parts 4038-1 and 4038-2. This is why 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 there is a constant communication between the channel 4032 of the axle and the channel 4035 of the connecting rod 4033. The use of an ESVT system may be possible.

If a bearing 4039 has a sliding fit with said hub 4038-1/4038-2, e.g. a squeeze fit with an axle 4040, said communication may occur as hub 4038 rotates about said axle. is interrupted when The use of a CT system may be possible. Figure 92A shows that around a main motor shaft 4094 having a central axis 5000, the pistons 4091 are identical;
Three cylinder motors 4090 moving in a circular chamber 4092 arranged parallel to each other
is schematically shown. Chambers 4092 are interconnected by housing 4095, and gearbox 4093 is mounted on the assembly by bolts 4096, springs 4097, and washers 4098. Main motor shaft 4094 of motor 4090 communicates directly with shaft 5004 of gearbox 4093. The gearbox 4093 includes a drive shaft 5000. The gearbox 4093 is installed in the opposite direction. Although not shown, it is alternatively possible for the main motor shaft 4094 to pass through the clutch when the clutch is pressed on a wheel (not shown), such as a flywheel that is in constant communication with the main motor shaft 4094. A clutch may be inserted between the shaft 5004 of the gearbox 4093 and the communicating main motor shaft 5004. When the clutch is not pushed onto the flywheel, the motor 4090 is free to rotate from the shaft 5004 of the gearbox 4093 and free to rotate from the outer shaft 4099 of the gearbox 4093. A pressure management system 5001, preferably an ESVT system in communication with a channel 5002 communicating with an enclosed space 5003 of each piston 4091 and an interior 5006 of each piston. Bolts 5004 (springs and washers) attach the two chamber parts 4092-1 and 4092-2 together for each chamber 4092. The pistons 4091 transmit their torques through the hub 5005 to the main motor shaft 4094, for example according to FIGS. 90A-C or FIGS. 90I, J.

FIG. 92B shows diagrammatically a three-cylinder motor 5010 with pistons 5011 moving in circular chambers 5012. Said chambers 5012 are identical and arranged parallel to one another around the main motor shaft 5013. A housing plate 5017 holds the chambers 5012 together. The torque generated by the pistons 5011 is transmitted by hubs 5019 through connecting rods (50xx) to the main motor shaft 5013, for example according to the figures. according to fig. 90A-C or fig. 90A-C. 90I, J or according to fig. 91A-D. On said main motor shaft 5013, on each side, assembled is a variable pitch wheel 5014 connected by a belt 5021 to a corresponding wheel 5015 on the vehicle axle 5016, shown with a high pitch on the side of the motor 5010 and a low pitch (
The vehicle is moving rapidly). Distance x is shown not changing as the pitch of the wheels 5014 and 5015 changes, which may be any pitch between the high and low pitches. A channel 5019 in the center of the main motor communicates directly with a pressure management system 5020, preferably an ESVT system. Not shown is an inverted arrangement to allow the vehicle to move backwards as well as forwards.

FIG. 92C is the same as FIG. 92B, but shows a small pitch of the wheel 5014' on the side of the motor 5010 and a high pitch of the wheel 5015' on the side of the wheel axle 5016 (the vehicle is moving slowly).

FIG. 93A shows a schematic representation of a three cylinder motor 5020 with chambers 5021 rotating around a central axis 5022. The chambers 5021 are connected to the central axis 5022 by corner brackets 5023, 5023' on each side of the chambers 5021, respectively, so that the torque generated by the chambers 5021 is transmitted to the central axis 5022 through the corner brackets. Because the central axis 5022 includes a part 5022' on the outside of each hub 5034 of each piston 5025, connected only by the bracket sites 5023, 5023', and further includes a bearing (5033) including a part (5033') corresponding to a part of the central axis (5022). The central axis 5022 communicates with an external gearbox 5024 through a gear wheel 5028. The gear wheel communicates with a gear wheel 5029. Said gear wheel 5029 is in indirect communication with the drive shaft axis 5030. Direction of rotation 5031 of the drive shaft axis 5030. Each chamber 5021 comprises a piston 5025 and a ring 5026, which acts as a flywheel and is located furthest from the central axis 5022. Said piston 5025 is assembled to an inner shaft 5032 by means of a hub 5034. Said inner shaft 5032 is mounted by means of mountings 5035, 5035', which are respectively attached to the vehicle and to the gearbox. Between the inner shaft 5032 and the shaft 5022 is a bearing 5033 (see enlarged view). A pressure management system 5027, preferably an ESVT system. A communication 5036 of the pressure management system 5027 with a channel 5037 in said inner shaft 5032. Said channel 5037 communicates with a channel 5039 in a connecting rod 5040 (shown diagrammatically), which communicates with a space 5038 in the piston 5025 .

FIG. 93B shows an enlarged view (4:1) of the left corner of the central shaft 5022 and the bearing 5033 between the central shaft 5022 and the inner shaft 5032. Lighting equipment 5035.
107 Description of the Preferred Embodiment Figure 100 shows a so-called indicator diagram. This figure schematically shows the adiabatic relationship between the pressure p and the pump stroke volume V of a conventional single stage unidirectionally actuated piston pump having a cylinder with a fixed diameter. The increase in actuation force per stroke can be read directly from the figure and is quadratic with respect to the cylinder diameter. The pressure p, and therefore the operating force F, increases normally during the stroke until the valve of the body to be inflated opens.

FIG. 102A shows an indicator diagram of a piston pump according to the invention. The diagram of the pressure p is similar to that of a conventional pump, but the operating force is different and showed that it completely depends on the selected area of the cross section of the pressurized chamber. This depends entirely on the specifications. For example, the operating force may not exceed a certain maximum value, or the magnitude of the operating force may vary according to ergonomic requirements. This is particularly required if the manual pump only transports the medium without significant changes in pressure, as is the case, for example, with water pumps. The longitudinal and/or cross-sectional shape of the pressurized chamber may be any kind of curve and/or line. It is also possible to increase the cross section, for example by increasing the pressure (FIG. 102B). An example of the operating force is the dashed thick line 1 or 2. The different wall possibilities marked 1 and 2 correspond to the 1st and 2nd rows mentioned above in the figure. The A section concerns a pump with only the piston moving, and the B section concerns a pump with only the chamber moving. It is also possible to combine both movements at the same time.

FIG. 102B shows an example of an indicator diagram of a piston pump having a chamber with a cross section that increases with increasing pressure.
Figures 103A, B, C, D show details of the first embodiment. The piston moves within a pressurized chamber that includes a cylindrical and a conical part with a cylindrical cross section with a diameter that decreases as the pressure of the gas and/or liquid medium increases. This is based on the specification that the driving force must not exceed a certain maximum value. The transition between the various diameters is gradual without discrete steps. This means that the piston can easily slide within the chamber and adapt itself to the changing area and/or shape of the cross-section without loss of sealing ability. If it is necessary to increase the pressure and reduce the operating force, the cross-sectional area of the piston is reduced and the circumferential length is accordingly reduced. The reduction in circumferential length is based on compression or relaxation up to the buckling level. The longitudinal section of the piston means is trapezoidal at a variable angle with the wall of the pressurized chamber, for example less than 40°, and cannot be deflected rearwardly. The dimensions of the seal change in three dimensions with each stroke. A support of the piston means, for example a disc or an integral rib in the sealing means, arranged on the non-pressure side during the pumping stroke of the piston, protects against deflection under pressure. Also, the load part of the piston means, for example a spring washer with several segments, may be mounted, for example on the pressure side of the piston. This tightens the flexible seal against the wall. This is useful if the pump has not been used for some time and the piston means has been bent for some time. By moving the piston rod, the sides of the trapezoidal section of the sealing part of the piston means are pushed axially and radially, so that the sealing edge of the piston follows the reduced diameter of the pressurized chamber. At the end of the stroke, the bottom of the central chamber is raised to reduce dead room volume. The piston rod may be primarily guided by a cap that locks the pressurized chamber. When the piston seals to the walls of the chamber in both directions of its movement, the piston rod is provided with an inlet channel with a spring force-operated valve that is closed in case of overpressure in the chamber, for example. If the load part of the piston means is not used, this separate valve is unnecessary. In the design of the pump according to the invention, the pump components are optimized for working forces. The inner diameter of the pump is on the main part of the pump chamber length which is larger than existing pumps. As a result, the inlet volume is large, even though the volume of the remainder of the chamber is smaller than that of existing pumps. This allows the pump to pump faster than existing pumps, but the maximum operating force required is significantly reduced and lower than levels that consumers have reported as comfortable. The length of the chamber can be shortened, making the pump practical even for women and teenagers. The stroke volume is still larger than that of existing pumps.

FIG. 103A shows a piston pump with a pressurized chamber 1 having parts of wall sections 2, 3, 4 and 5 of different areas of its cross section. The piston rod 6 cap 7 stops the piston means and guides the piston rod 6. Transition between the cross sections of walls 2, 3, 4, 5 16, 17, 18 longitudinal central axis 19 of chamber 1. The first piston 20 and the last piston 20' of the pump stroke.

Fig. 103B shows a sealing part 8 made of elastic material and a load part 9 consisting of, for example, a spring washer with segments 9.1, 9.2, 9.3 (not shown) and a support part 10 of the piston means attached to the piston rod 6 between two parts of the locking means 11. The piston rod 6 has an inlet 12 and a valve 13. Angle α1 between the sealing part 8 of the piston means and the wall 2 of the pressure chamber 1. Sealing edge 37. Distance a is the distance from the sealing edge 37 to the central axis of the chamber 1 in the cross section at the beginning of the stroke.

Figure 103C shows the outlet channel 14 of the means 15 for reducing the dead room volume. The angle α2 between the seal 8' of the piston means and the wall 5 of the pressurized chamber 1. The distance a' is the distance from the seal edge 37 to the central axis of the chamber 1 in the cross section at the end of the stroke. It is shown that the distance a' is about 41% of the distance a. Load portion 9'.

FIG. 103D shows that the cross section is selected so that the operating force is kept nearly constant, and ergonomic requirements (
For example, the chamber (φ inner 60 mm) of the floor pump according to the present invention is selected according to FIG.
19.3 mm, length 500 mm). Other force magnitudes can also be chosen. This only gives a starting point for the quantification of the floor pump according to the invention, since a constant operating force may not be ergonomically correct. For comparison, an existing low-pressure floor pump (φ
1 shows a cross section of a floor pump (φ 32mm, length 470mm) in dotted line and a cross section of an existing high pressure floor pump (φ 27mm, length 550mm) in dotted line. It is clearly shown that both floor pumps according to the invention have a larger stroke volume than the existing pumps, and therefore faster inflation tires and lower operating forces. The chamber according to the invention can be adapted to ergonomic requirements during the entire stroke.

Figures 104A, B, C, D, E, F show details of a second preferred embodiment. The sealing portion of the piston means is made of an elastically deformable material supported by a support means capable of rotating about an axis parallel to the central axis of the chamber.

This movement results in a larger area of the sealing part, which is in the chamber at higher pressure. The load part against the support initiates the movement of the support means. The load part in the form of a flat-shaped spring can change its dimensions in a direction perpendicular to the center line of the chamber. The higher the pressure in the chamber, the more rigid the spring becomes. It can also be a spring on the axis about which the support means rotates. The length of the sealing part is increased by decreasing its diameter. It is an elastically deformable material, slightly compressible, for example rubber. At the beginning of the stroke, the piston rod therefore protrudes from this sealing means. If another material for the sealing part is chosen, its length can remain unchanged or be reduced by decreasing its diameter.

Figure 104A shows a piston pump with a pressurized chamber 21 with parts of different cross-sectional area. The chamber has cooling ribs 22 on the high pressure side. The chamber can be (injection) molded. A piston rod 23. A cap 24 guides said piston rod. A piston 36 at the beginning and a piston 36' at the end of the pump stroke.

FIG. 104B shows an elastically deformable seal portion 25 (
(not stretched). A portion 27 of the piston rod 23 projects from the seal portion 25. The support portion 28 is suspended by a ring 29 fixed to the piston rod 23. Support 28 can rotate around axis 30. The load portion 31 includes a spring fixed to the piston rod 23 within the hole 32. Sealing edge 38.

Figure 104C shows that part 27 of piston rod 23 is substantially covered by an elastically deformed sealing means 25', which now increases its length and its diameter. It is decreasing. Sealing edge 38'. Distance a between the sealing edge 38 of the chamber and the central axis 19
' is about 40% of the distance a in the cross section shown.

Figure 104D shows section AA of Figure 104B. The load portion 31 is fixed at one end of the bore 32 of the piston rod 23. Support part 28 and ring 29. The support is stopped by a stop surface 33 (not stretched). The support part 28 is guided by guide means 34 (not shown).

Figure 104E shows node BB of Figure 104C. The support means 28 and the load means 31 are moved towards the piston rod 23. Rib 22.
FIG. 104F shows an alternative loading means 31. A spring 35 is provided on each shaft 30. Figures 105A, B, C, D, E, F, G, H show details of the third embodiment. It is a variant of the first embodiment. The seal includes a flexible impermeable membrane for gaseous and/or liquid media.
This material can be resized in three directions without bending. This seal is attached to an O-ring that seals to the chamber wall. O-rings can be used as loading means, e.g.
The wall is loaded by surrounding springs. The O-ring and spring are further supported by support means that are rotatable about an axle fixed to the piston rod. This support means can be spring loaded.

Figure 105A shows a longitudinal section of a piston pump analogous to that of Figure 103A, with piston 49 at the beginning and piston 49' at the end of the pump stroke.
105B shows the piston means at the start of the stroke with sealing means 40 (e.g. stressed skin), which is fixed to sealing means 41 (e.g. an O-ring). This O-ring is loaded by a spring 42 arranged around sealing means 41 and sealing means 40. Central axis 39 of spring 42. O-ring 41 and/or spring 42 are supported by support means 43 rotatable on axis 44 attached to piston rod 45.

It is arranged perpendicular to the central axis 19. It contains a quantity of separate members 43', which are loaded in compression during the (compression) pump stroke. These are arranged around and supported by the sealing means 40, 41 and the loading means 42. The supporting means 43 can be loaded by a spring 46. The angle β between the wall of the chamber 2 and the supporting means 43, the piston rod 45, does not have an inlet or a valve. As an alternative to the spring 42 (not shown), a supporting ring and/or a loading ring in the form of a spring can be attached to the O-ring. Sealing edge 48.

Figure 105C shows the piston means at the end of the stroke. The sealing means 40', 41' are thicker 40, 41 than at the beginning of the stroke. Spring 46'. The angle β2 between the wall surface 5 and the support means 43 is the end of the stroke. The distance a' between the sealing edge 48 and the central axis 19 of the chamber is approximately 22% of the distance a at the beginning of the stroke in the cross section shown. Smaller distances are possible, for example 15%, 10% or 5%, depending only on the structure of the suspension of the piston on the piston rod. Therefore, this is also valid for all other embodiments.

105D shows section CC of FIG. 105A with support means 43, shaft 44, and bracket 47. FIG. Figure 105E shows section DD of Figure 105A.
Figure 105F shows two positions of piston 118 of Figure 105G and piston 118' of Figure 105H within the chamber.

FIG. 105G shows a piston made of a composite of materials. It includes a skin 110 and fibers 111 of elastic impermeable material. The fiber architecture takes a dome form when subjected to internal pressure. This shape stabilizes the movement of the piston. Alternatively, the sealing means may include a liner, a fiber, and a cover (not stretched). If the liner is not tight, an impermeable skin may be added (not depicted). All materials on the compression side of the piston are adapted to the specific environmental requirements of the chamber. The skin is attached to the sealing part 112. Within the skin and sealing part, a spring force ring 113 is attached, which can be elastically deformed in its plane and can increase the load 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 compressed to shape 115 when there is still full overpressure. Shape 110' is the result when the overpressure drops after, for example, media is released.

Figures 106A, B, C show details of the fourth embodiment. The piston means comprises, for example, a rubber tube with a reinforcement in the form of a textile thread or cord wound around it. The neutral angle (= so-called braid angle) between the tangent of the reinforcing winding and the central fine part of the hose is mathematically calculated to be 54°44'. The hose under internal pressure does not change dimensions (length, diameter) assuming that the reinforcing bar does not stretch. In this embodiment, the diameter of the piston means decreases in proportion to the decreasing diameter of the cross section of the chamber as the pressure increases. The braid angle should be wider than neutral. The shape of the main part of the longitudinal cross section of the pressurizing chamber is approximately conical due to the behavior of the piston means. At the end of the pump stroke, when the compressed medium is removed from the chamber, the piston means increases its diameter and decreases its length. The increase in diameter is not a practical problem. The sealing force from the piston to the wall of the pressurizing chamber should be increased by increasing the pressure. This can be done, for example, by selecting the braid angle so that the diameter of the piston is a little smaller than the decrease in the diameter of the cross section of the chamber. Therefore, the braid angle can also be chosen smaller.

than neutral or neutral. In general, the choice of braid angle depends entirely on the design specifications, therefore the braid angle may be wider and/or smaller and/or neutral. The braid angle may even vary depending on the location in the piston. Another possibility is that within the same cross section of the piston there are several reinforcing layers with the same and/or different braid angles. Any kind of reinforcing material and/or reinforcing pattern can be used. The location of the reinforcing layer can be any location within the longitudinal cross section of the piston. The amount of lining and/or cover may be multiple. Also there may be no cover. The piston means may also include load means and support means, for example those shown above. In order to be able to accommodate larger changes in the cross section of the chamber, a slightly different structure of the piston means is necessary. The cone is now composed of 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 may also be fixed to the piston rod itself. The pattern of the fibers is designed such that, for example, the higher the pressure, the higher the pressure in the chamber of the pump where the medium is to be compressed. Of course, other patterns are possible depending on the specifications. They deform the skin of the cone, making it adapt itself to the cross section of the chamber. The fibers can be loose on the liner, loose in the channel between the liner and the cover, integrated in one of the two, or integrated in both. If there is still no pressure under the cone, it is necessary to have a loading means to obtain a proper seal to the wall. Loading members, for example spring force members in the form of rings, plates, etc., may be built into the skin, for example by inserting them in the moulding process. The suspension of the cone on the piston rod is better than in the previous embodiment, since the piston is now loaded by tension. It is therefore more balanced and less material is required. The skin and cover of the piston may be made of an elastically deformable material adapted to the specific environmental conditions, while the fibres may be elastic or rigid and made of suitable materials.

FIG. 106A shows a longitudinal section of the pump with chamber 60. The walls 61, 62, 63, 64, 65 are both cylindrical 61, 65 and conical 62, 63, 64. The transitions between said parts 66, 67, 68, 69 are the piston 59 at the beginning of the pump stroke and the piston 59' at the end.

Figure 106B shows piston means 50, which is a hose with reinforcement 51. The hose is secured to piston rod 6 by clamp 52 or the like. Piston 6 has ribs 56 and 57. Rib 56 prevents movement of:

The piston means 50 moves towards the cap 7 relative to the piston rod 6 and the rib 57 prevents the piston means 50 from moving away from the cap 7 relative to the piston rod 6. Other configurations of fittings are also possible (not shown). On the outside of the hose, the projection 53 seals against the wall 61 of the chamber 60. In addition to the reinforcement 51, the hose is provided with a lining 55. A cover 54 is also shown by way of example. The shape of the longitudinal cross-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 may be designed such that the change in diameter occurs only through radial change (not shown).

Figure 106D shows the piston 189 of Figures 106E and 189' of Figure 106F at the beginning and end of the pump stroke in the chamber of Figure 106A, respectively.
Figure 106E shows a piston means having approximately the general shape of a cone with an apex angle of 2ε1. Indicates when there is no overpressure on the sides of the chamber. It is mounted atop the piston rod 180. The cone is open on the pressure side of the piston. The cover 181 includes a sealing part shown as a protrusion 182 with a sealing edge 188, an inserted spring force member 183, a fiber 184 as a support means, and a liner 185. Member 183 loads the cover so that, in the absence of overpressure on the sides of the chamber, said protrusion 182 seals against the walls of the chamber. Fibers 184 may be present within channels 186 and are shown disposed between cover 181 and liner 185. Liner 185 may be impermeable, and if not, a separate pressure side layer 209 (not shown) is mounted over liner 185. The fibers are attached to the piston rod 180 and/or to each other at the top 187 of the cone. This also applies to the lower end of the piston rod 180.

Figure 106F shows the piston means at the end of the stroke: the upper angle is now 2ε2 and the distance a' between the sealing edge 188 of the chamber and the central axis 19 is about 44% of the distance a at the start of the stroke in the cross section shown.

Fig. 107A, B, C, D, E show details of a fifth embodiment of the pump, the piston being constructed as another composite structure, comprising a very flexible and very elastic basic material in all three dimensions. If it is not sealed by itself, it can be sealed, for example, by a flexible membrane on the pressurized side of the piston means. The axial stiffness is achieved by several integrated stiffeners. The stiffeners are present in a pattern in the cross section, which optimally fills this cross section, while the intermediate distances are shorter the smaller the diameter of the cross section, which in most cases means a higher pressure in the pressurized chamber. In the longitudinal part of the piston, the stiffeners are located at several angles between the axial direction of the piston means and the direction of the surface. The higher the pressure rate, the smaller these angles are, approaching the axial direction. Thus, the forces are transmitted to the support means, such as washers connected to the piston rod. The piston means can be mass-produced and is cheap. The stiffeners and, if necessary, the sealing means in the form of said flexible membrane, may be injection-molded together with said basic material. For example, the stiffeners can be joined together at the top, which makes handling easier. It is also possible to create a membrane by "burning" into the base material during or after injection molding. This is particularly useful when the base material is a thermoplastic. The hinges must not be "burned".

Figures 107F, G, H, I, J, K, L, M show an embodiment of a chamber and a sixth embodiment of a piston, which fits into this chamber. The sixth embodiment of the piston is one variant of Figures 107A, B, C, D, E. If the change between two positions in the direction of movement of the cross-sectional area of the piston and/or chamber is continuous, but still very large, causing leakage, it is advantageous to minimize the change in other parameters of the cross section. This can be illustrated for example by using a circular cross section (fixed shape), i.e. the circumference of the circle is πD
and the area of the circle is 1/4πD2 (D = diameter of the circle). That is, a reduction in D gives only a linear reduction in the circumference and a quadratic reduction in the area. It is also possible to maintain the circumference, just reduce the area. Also, if the shape is fixed, e.g. circular, there is a certain minimum area. Advanced numerical calculations where the shape is a parameter can be done using the Fourier series expansions described below. The cross section of the pressurized chamber and/or piston can have any shape, which can be prescribed by at least one curve. The curves are closed and can be roughly defined by two unique modular parameterized Fourier series expansions, one for each coordinate function.

ここで、

here,

Cp = ｆ(x)の余弦重み付け平均値
dp = ｆ(x)の正弦重み付け平均値、
p = 三角法の細かさの次数を表す。

Cp = cosine weighted average value of f(x)
dp = sine weighted average value of f(x),
p = represents the degree of trigonometry granularity.

Figures 107F, 107K show examples of said curves by using different sets of parameters in the following formulas. In these examples, only two parameters are used. If more coefficients are used, it is possible to find optimized curves that meet other important requirements. For example, curve transitions with the maximum radius of the curve and/or, for example,
It is possible to find the maximum possible tension in the seal that does not exceed a certain maximum value under a given prism. As an example, Figures 107L and 107M show optimized convex and non-convex curves used for possible deformations of bounded regions in a plane, with the constraint that the length of the boundary curve is fixed and its numerical curvature is minimized. Using the starting region and the starting boundary length, it is possible to calculate the minimum possible curvature for the desired target region.

The pistons shown in the longitudinal section of the chamber are primarily drawn if the boundary curve of the cross section is circular. That is, if the chamber has a non-circular cross-section, for example in FIGS. 107F, 107K, 107L, 107M, the shape of the longitudinal cross-section of the piston may be different.

All kinds of closed curves can be described by this formula, for example the C-curve (see PCT/DK97/00223, Figure 1A). One feature of these curves is that when lines are drawn from the mathematical poles in the cross section,
It is easier to create a piston or chamber if the cross-sectional curve is symmetrical about a line in the cross-sectional plane that passes through the mathematical pole. Such a regular curve can be approximately defined by the following single Fourier series expansion:

ここで、

here,

Cp = ｆ（ｘ）の重み付き平均値、
p =三角法の細かさの次数を表す。

Cp = weighted average value of f(x),
p = represents the degree of fineness of trigonometry.

When a line is drawn from a mathematical pole, it always intersects the curve only once. The particular formed sector of the cross section of the chamber and/or piston may be approximately defined by the following equation:

ここで、

here,

Cp = ｆ（ｘ）の重み付き平均値、
p =三角法の細かさの次数を表す。

Cp = weighted average value of f(x),
p = represents the degree of fineness of trigonometry.

This cross section in polar coordinates is approximately expressed by the following equation.

ここで、

ro>=0,

a>=0,

m>= 0, m∈ R,

n>= 0, n∈ R,

0<= φ<= 2π,

ここで、
r = 活性ピンの円形断面の"花弁"の限界、
ro = 活性ピンの軸の周りの円形断面の半径、
a = "花弁"の長さのスケールファクター
r_max = r₀ + a
m = 「花弁」幅の定義のためのパラメータ
n =「花弁」の数の定義のためのパラメータ
φ = 曲線を境界する角度

注入口は、ピストン手段のシール部の性質のため、ストロークの端部の近くに配置される。これらの特定のチャンバは、射出成形によって、また、例えば、アルミニウムシートが、工具キャビティ内で強制的に加熱されて空気圧によって加熱され、プレスされるか、または工具運動も用いて形成される、いわゆる超塑性成形方法の使用によって製造することができる。

here,

ro>=0,

a>=0,

m>= 0, m∈R,

n>=0, n∈R,

0<= φ<= 2π,

here,
r = limit of the "petals" of the circular cross section of the active pin,
ro = radius of circular cross section about the axis of the active pin;
a = "petal" length scale factor
_rmax = _r0 + a
m = parameter for defining the "petal" width
n = Parameter for defining the number of "petals" φ = Angle that bounds the curve

The inlet is located near the end of the stroke due to the nature of the sealing part of the piston means. These particular chambers can be manufactured by injection moulding and also by using the so-called superplastic forming method, where for example an aluminium sheet is heated and pressed by air pressure, forced into a tool cavity, or formed using tool movements as well.

FIG. 107A shows a piston pump with a pressurized chamber 70 in longitudinal section with a cylindrical part 71, a transition 72 to a continuous concave curve 73, a transition 74 to a substantially cylindrical part 75. Piston means 76, 76' are each shown at the beginning of the end of the pump stroke. A check valve 78 can be attached to the end of the outlet channel 77 (not shown).

FIG. 107B shows the piston means 76 with an elastic material 79, which gives the longitudinal part of the piston an approximately conical shape at low pressure. The material 79 also serves as a load means. The bottom part is provided with a radially foldable sealing means 80, which also serves partially as a loading means. The main support means consists of reinforcements 81, 82, the reinforcement 81 mainly supports the sealing edge 83 of the piston means on the wall of the pressure chamber 70, the other reinforcement 82 transfers the load from the sealing means 80 and the basic material 79 to the support means 84, which is for example a washer that is itself supported by the piston rod 6. The sealing means 80, in this position of the piston means 76, is still slightly folded, the higher the pressure in the chamber 70, so that the fold 85 loads the sealing edge 83. The reinforcements 82 are joined to each other at the top by a joint 86. In this position of the piston means 70, the stiffeners 81 and 82 have an angle with the central axis 19 between γ and δ, where δ is approximately parallel to the central axis 19 of the pressure chamber 70. Angle φ1 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 is
Folded together, the elastic material 79 is tightened together so that the reinforcements 81, 82 are oriented approximately parallel to the central axis 19. The angle φ2 between the surface of the piston means 76' and the central axis 19 is positive, but approximately zero. distance a'
The distance between the sealing edge 83 and the central axis 19 in the cross section shown is 39% of the distance a at the beginning of the stroke. The sealing means is 80'.

FIG. 107D shows a cross section EE of the piston means 76 showing the basic elastic material 79, reinforcements 81, 82 and folds 87 of the sealing means 80. piston rod 6
FIG. 107E shows a cross-section FF of the piston means 76', showing the basic elastic material 79, reinforcements 81, 82 and folds 87 of the sealing means 80. What is clearly shown is that the elastic material 79 is squeezed together.

Figure 107F shows a series of cross-sections of the chamber. In this region, the area decreases at a given step, but the perimeter is constant, and these are defined by two unique modular parameterized Fourier series expansions, one for each coordinate function. At the top left there is a cross-section that is the starting cross-section of said series. The set of parameters used is shown at the bottom of the figure. This series shows a decreasing area of the cross section. The bold numbers in the figure indicate that the cross-sectional area of the different shapes is reduced, and the cross-sectional area of the corner is left as the size of the starting region.

The area of the shape on the right side of the bottom of the cross section is approximately 28% of the area on the left side of the top.
FIG. 107G shows a longitudinal cross-section of chamber 162, the cross-sectional area of which varies with the remaining circumference along the central axis.

Piston 163. The chamber has parts of different cross-sectional areas of its cross section in wall sections 155, 156, 157, 158. Transitions 159, 160, 161 between said wall sections. Sections GG, HH
, II are shown. Section GG has a circular cross section, while section HH 152 has about 90-70% of the area of section GG.

FIG. 107H is shown as a comparison cross-section GG 150 and cross-section H-H 152 of FIG. 107G and in dotted lines. The area of cross section H-H is approximately 90 to 70% of the area of cross section G-G. 151 smoothed transitions. Also shown is the smallest part of the chamber, which has approximately 50% of the cross-sectional area of section G-G.

Figure 1071 is shown as a comparative cross-section GG and in cross-section II and dotted lines in Figure 107G. The area of section II is approximately 70% of the area of section GG. Transition 153 is made smooth. Also,
The smallest part of the chamber is also shown.

FIG. 107J shows a modification of the piston of FIGS. 107A-C at cross section HH from FIG. 107G. Since the piston is made of a resilient material and is also impermeable, no separate sealing means are required. The distances c and d are different and depend on the deformation of the piston in the same cross section HH.

Figure 107K shows a series of cross sections of a chamber, where the area decreases at certain steps but the perimeter remains constant, and these are defined by two unique modular parameterized Fourier series expansions, one for each coordinate function. At the top left is the cross section that is the starting cross section for said series. The set of parameters used is shown at the bottom of the figure. While this series shows a decreasing area of the cross sections, it is also possible to increase these areas by maintaining the perimeter constant. The bold numbers in the figure indicate the decreasing cross sections of different shapes, with the cross sections at the corners being left as the size of the starting region.

The size of the bottom right cross-sectional area is approximately 49% of the starting region size.

upper left.

yで指定された長さは、次の式で決定されます。

ここで、
r = 最小曲率半径
L=境界長=定数
A1 = 開始ドメイン領域A0の減少値
図103Dからの例として、半径30のディスクの面積および境界長に対応するドメイン領域A0= π(30)2および境界長L=60π=188.5。長さは一定であることが必要であるが、領域は
指定される値A1まで減少する。所望の最終構成は、面積A1 = π (19/2)2 = 283.5 とする。ここで、境界曲線の可能な限り最小の曲率をもつ凸曲線は、次のようになる。 Figure 107L shows an optimized convex curve for a constant length of the boundary curve and the smallest possible curvature. The general formula for the minimum radius of curvature corresponding to the maximum curvature of the diagram shown in FIG. 107L is as follows.

The length specified by y is determined by the following formula:

here,
r = minimum radius of curvature
L=boundary length=constant
A1 = Decrement value of starting domain area A0 As an example from Figure 103D, domain area A0 = π(30)2 and boundary length L = 60π = 188.5, which corresponds to the area and boundary length of a disk of radius 30. The length needs to be constant, but the area decreases to the specified value A1. The desired final configuration has an area A1 = π (19/2)2 = 283.5. Here, the convex curve with the smallest possible curvature of the boundary curve is:

r = 1.54
Kappa = 1/r = 0.65
x = 89.4

The curves in the diagram are not to scale, the diagram illustrates the principle only.
The curve can be further optimized by replacing a straight line with a curved line, which may improve sealing to the wall of the piston.

xで特定された長さは、次の式で決定されます。

ここで、
r ＝ 最小曲率半径
L=境界長=定数
A1＝開始ドメイン領域A0の値
境界曲線の可能な限り最小の曲率を有する非凸曲線(ストリング状中間二重曲線の明瞭な
修正を伴う)
r = 6.3
κ = 1/r = 0.16
x = 42
図の曲線はスケールではなく、図は原理のみを示している。 FIG. 107M shows a non-convex curve optimized for a certain 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 diagram shown in FIG. 107L is as follows.

The length specified by x is determined by the following formula:

here,
r = minimum radius of curvature
L=boundary length=constant
A1 = value of the starting domain area A0 A non-convex curve with the smallest possible curvature of the boundary curve (with a clear modification of the string-like intermediate double curve)
r = 6.3
κ = 1/r = 0.16
x = 42
The curves in the diagram are not to scale and the diagram illustrates the principle only.

Figures 108A,B,C show a seventh embodiment of the pump, where the piston means is constructed as another composite structure containing a compressible medium, e.g. a gaseous medium like air (only non-compressible mediums are possible, e.g. a liquid medium like water or a combination of compressible and non-compressible media) in a sealed chamber, constructed for example as a reinforced hose. The lining, reinforcement and cover at the pressure side of the piston means can be different from that of the non-pressurized side, where the skin is formed as a pre-formed skin and can retain this shape during the pump stroke. Also, the skin is made of two or more pre-formed parts, one at the non-pressurized side of the piston means and one at the pressure side (see part X(Y+Z) in Figure 108B). During the pump stroke, the two parts hinge to each other (Figure 108B XY
and ZZ). The adaptation of the seal edge to the chamber in cross section can cause a change in the cross section of the piston at the seal edge, which can cause a change in volume within the piston. This volume change can cause a change in the pressure of the compressible medium, which can change the sealing force. In addition, the compressible medium acts as a support in transmitting the load on the piston to the piston rod.

FIG. 108A shows a longitudinal section of a pressurized chamber 90 with a continuous convex curve 91 with a piston 92 at the beginning of the pump stroke and a piston 92' at the end thereof. The high pressure portion of chamber 90 includes an outlet channel 93 and an inlet channel 94 having both check valves 95 and 96, respectively. For low pressure purposes, check valve 95 can be removed.

FIG. 108B shows piston 92 vulcanized directly onto piston rod 97, including compressible medium 103 within lining 99, reinforcement 100, and cover 101. The X section of the skin 99, 100, 101 is preformed in the same way as the Y section and Z section of the pressure section of the piston means 92. Hinge XY is shown between the X and Y portions of the skin. Part X has an average angle η1 with the central axis 19 of the pressurized chamber 90. Parts Y and Z are connected to each other and lie in the middle of the angle κ1. This angle κ1 is chosen such that the force is directed primarily to the piston rod. The angle λ between the Y' and Z' parts is chosen such that the greater the force in the chamber, the more this part is perpendicular to the central axis. ZZ is hinged between the Z halves and a sealing edge 102 is provided.

FIG. 108C shows the piston at the end of the stroke. Section X' of the skin has an angle η2 with the central axis, sections X' and Y' have an intermediate angle κ2, and an almost constant angle λ between sections Y' and Z'. The half angle of section Z is almost zero. The distance a' between the sealing edge 102 of the chamber and the central axis 19 in the illustrated cross section is about 40% of the distance a at the beginning of the stroke.
The sealing edge 102' and the compression media 103'.

Figure 109A, B, C, D show eight embodiments of pistons that can change the dimensions and the details of the combination of a pressurized chamber with fixed dimensions. The piston is an expandable body that fills the cross section of the chamber. During the stroke, the dimensions of the sealing edge and its vicinity can change constantly. The material can be a composite of an elastically deformable liner and a support means, for example, fibers (for example, glass, boron, carbon or aramid), fabrics, fillings, etc. Depending on the fiber architecture and the overall load generated on the piston (the piston is shown to have a slight internal overpressure), the piston can result in any shape between approximately spherical, or approximately elliptical (shaped like a "rugby ball"), or other shapes. For example, a reduction in the cross-sectional area of the chamber causes a reduction in the size of the expandable body in that direction, and a reduction in three dimensions is possible because of the fiber architecture based on the "trellis effect" where the fibers are sheared independently from each other in layers. The cover is also made of an elastically deformable material suitable for the specific environmental conditions in the chamber. If the liner or cover is impermeable, it is possible to use a separate bladder inside the body to contain the gas and/or liquid medium inside the body. The support means, e.g. fibers, can only give strength by themselves if the pressure inside the body is greater than outside, because they are in tension. This pressure condition is preferred to obtain a proper seal and life. Since the pressure in the chamber is constantly changing, the pressure inside the body should be the same, a little higher, or at any point of the pump stroke, always higher by keeping it constant. The last solution can only be used for low pressures, otherwise the piston would jam in the chamber. To increase the pressure in the chamber, a pressure of 10 ...

It is necessary to make the internal pressure change according to the pressure fluctuations in the chamber. + should be a little higher. This can be done in several different configurations, based on the principle of changing the volume and/or pressure of the medium in the piston and/or the principle of changing the temperature in the medium, i.e.
This can be achieved by a loading adjustment means. Other principles are possible, for example a suitable choice of material for the skin of the piston of a particular rubber type, the E module which defines the deformability, or a suitable choice of the relative amount of the compressible part of the volume in the inflatable body and its compressibility. Here, an incompressible medium is used in the piston. Due to the change in the size of the cross-sectional area at the sealing edge, the volume of the piston can change, since the size of the piston in the direction of movement is constant. This change causes the incompressible medium to flow between the spring-force actuated piston in the hollow piston rod. The spring-force actuated piston can also be located in other places. A constant sealing force is obtained by the combination of the pressure due to the change in the volume of the piston and the pressure due to the spring force. The spring force acts as a fine adjustment to the sealing force. An improved load adjustment can be achieved by replacing the incompressible medium by a particular combination of compressible and incompressible media, in which case the compressible medium acts as a load adjustment means. A further improvement is when the spring is replaced by the operating force of the piston in the chamber, which makes the piston retraction easier due to lower sealing force and lower friction. A temperature increase of the medium in the piston can be achieved especially if a medium is selected that can warm up quickly.

FIG. 109A shows a longitudinal section of the piston 146 of FIG. 109B at the beginning of the stroke and the pressure chamber of FIG. 108A at the end 146' of the stroke.
FIG. 109B shows a piston 146 in which the expandable body has a wall that includes a patterned fiber 130 such that the expanded body is a sphere. Cover 131 and liner 132. An impermeable bladder 133 is shown inside the sphere. The sphere is attached directly to the piston rod 120, which is locked at one end by cap 121 and at the other end by cap 122. The hollow channel 125 of the piston rod 120 has holes 123 on the side inside the sphere so that
A loading means, such as a compressible medium 124 contained within a sphere, is able to flow freely to and from the channel 125 .

The other end of the piston rod 120 channel 125 is closed by a movable piston 126 loaded by a spring 127. The spring is attached to piston rod 128. Spring 127 adjusts the pressure and sealing force within the sphere. Sealing surface 129 is in substantially linear contact with an adjacent wall of the chamber. The fibers are shown only schematically (in all drawings of this application).

Figure 109C shows the piston of Figure 109B at the end of its stroke with the smallest cross-sectional area. The sphere has a much larger sealing surface 134 that is uniform with the adjacent walls of the chamber. Once the incompressible medium 124' was squeezed out of the distorted sphere, the piston 126 moved relative to its position shown in FIG. 9B. To minimize frictional forces, the sealing surface cover has ribs (not shown) or a low-friction coating (as well as the walls of the chamber (not shown)
). Since neither caps 121 nor 122 can move along piston rod 120, the trellis effect is only part of the material surplus of the skin. The remaining portion is designated as a "shoulder" 135, which can significantly shorten life while increasing friction. Sealing edge 129'. The distance a' between the sealing edge 129' of the chamber and the central axis 19 in the illustrated cross section is approximately 48% of the distance a at the beginning of the stroke.

Fig. 109D shows improved adjustment of the sealing force by having a non-compressible medium 136 and a compressible medium 137 inside the sphere. The pressure of the medium is adjusted by a piston 138 with a sealing 139 and a piston rod 140 that is directly connected to the actuation force. The piston 138 can slide inside the cylinder 141 of the sphere. A stop 145 secures the sphere on the piston rod 140.

Figure 110A,B,C shows an improved piston where excess skin can be released due to the small cross section of the chamber, which means improved life and less friction. The method relates to the fact that the suspension of the piston on the piston rod can be moved and/or rotated on the piston rod to a position further away from the side of the piston where there is maximum pressure in the chamber. A spring between the movable cap and a stop on the piston rod serves as another load adjustment means.

FIG. 110A shows a longitudinal section through a chamber 169 of a pump according to the invention, each having two positions of a piston 168'.
FIG. 110B shows a piston with an inflatable skin having fibers 171 in at least two layers with a fiber structure that, when inflated, produces an approximately sphere-ellipsoid. The inside of the piston can be an impermeable layer 172, if the skin is not rigid. The medium is a combination of a compressible medium 173, e.g., air, and an incompressible medium 174, e.g., water. The skin 170 is attached to the end of the piston rod in a cap 175 fixed to the piston rod 176. The other end of the skin is fixed to a movable cap 177 that can slide on the piston rod 176. The cap 177 is pressed towards the pressurized portion of the chamber 169 by a spring 178 that is tightened at the other end towards a washer 179 fixed to the piston rod 176. The sealing edge 167.

Figure 110(C) shows the piston of Figure 110(B) at the end of the pump stroke. Spring 178' is compressed. This is also valid for non-compressible media 174' and compressible media 173'. The skin 170' is modified and now has a large sealing surface 167'. The distance a' between the sealing edge 167 and the central axis of the chamber is approximately 43% of the distance a at the beginning of the stroke.

Fig. 111 A, B, C show a piston with movable caps at both ends in the direction of movement on the piston rod to remove excess material. This is an improvement of the piston in one-way piston pumps, but it is possible to use the piston in dual action pumps, in which any stroke, and also the retraction stroke, is a pump stroke. The movement of the skin during the operation is indirectly limited by the stops of the piston rod. These are arranged so that the pressure of the medium in the chamber cannot peel the piston off the piston rod.

FIG. 111A shows a longitudinal section of the chamber with the modified piston 208 at the beginning and end of the stroke (208').
FIG. 111B shows a ninth embodiment of the piston 208. The skin of the sphere is equivalent to the skin of FIG. 10. The inner impermeable layer 190 is tightly squeezed to the cap 191 at the top and to the cap 192 at the bottom. The details of said caps are not shown, any kind of assembly method can be used. Both caps 191, 192 can translate and/or rotate over the piston rod 195. This can be done by different ways, for example by different types of bearings, not shown. The cap top 191 can only move upwards due to the presence of a stop 196 in the piston. The cap bottom 192 can only move down the step, since the stop 197 prevents it from moving upwards. The "adjustment" of the sealing force involves a combination of incompressible media 205 and a.

Compressible medium 206 within the sphere, spring force actuated piston 126 within the piston rod 195. The medium can flow freely through the holes 199, 200, 201 through the wall 207 of the piston rod. O-rings or similar 202, 203 in the upper and lower caps are
Seal caps 191 and 192, respectively, to the piston rods. Cap 204 is shown as an assembly threaded onto the end of piston rod 195 to tighten said piston rod. Similar stops can be placed at other locations on the piston rod depending on the required movement of the skin.

FIG. 111C shows the piston of FIG. 111B at the end of the pump stroke. The top cap 191 is moved a distance x'' from the stop 196 while the bottom cap 192 is pressed against the stop 197. Compressible medium 206' and incompressible medium 205'.

Figures 112A, B, C show an improved piston to the previous piston. This improvement must be related to a better adjustment of the sealing force by means of load adjustment, and in particular to a reduction in friction due to a smaller sealing contact surface due to a smaller cross-sectional area. The improved synchronization relates to the fact that the pressure in the piston is now directly influenced by the pressure in the chamber due to a pair of pistons on the same piston rod and is independent of the presence of an operating force on the piston rod. This can be particularly advantageous when the actuation force changes, for example during stops of the pump stroke, as the sealing force remains constant and no seal loss occurs. If the pressure in the chamber is reduced, at the end of the pump stroke, the frictional forces are reduced and therefore deflation becomes easier. In the case of a dual-operating pump, the load adjustment means can be influenced by both sides of the piston, for example by a double arrangement of this load adjustment means (not shown). The piston arrangement shown is in accordance with the specifications. For example, as the pressure within the chamber increases, the pressure within the piston increases. Other specifications may result in different arrangements. The relationship can be designed such that the increase differs from the linear relationship. The structure is a pair of pistons connected by a piston rod. The pistons may have equal areas, different sizes, and/or varying areas.

Due to the particular fiber architecture and the resulting total load, this shows a slight excess of internal pressure, and the shape of the piston in longitudinal section is a diamond-shaped figure. The two corners of this section act as sealing surfaces and reduce the contact area due to the smaller cross section of the chamber. The size of the contact surface can still be increased by the presence of a ribbed outer surface of the skin of the piston. The walls of the chamber and/or the outside of the piston may have a coating, such as nylon, or may be made of a low friction material.

Although not shown, for example, a chamber having the cross-sectional shape of FIG. 107F might have, for example, three separate pistons (in this case, by way of example) that each seal to each other and the boundary curves at a first circular cross-sectional area (FIG. 107F, top, left), while at another point on the longitudinal axis of the chamber, each seals to one of the three lobes and to each other (e.g., FIG. 107F, top, right), and at yet another point, each seals to only one of the three lobes.

FIG. 112A shows a longitudinal section of the piston-chamber combined with the tenth embodiment of the piston 222 at the beginning and end (222') of the stroke within the chamber 216.
FIG. 112B shows a piston whose main structure is described in the figure. 11B and 11C. The skin includes outer ribs 210. The inner skin and impermeable layer 190 is tightened at the top between the inner portion 211 and the outer portion 212, which are tightened together. At the bottom, a similar structure exists with an inner part 213 and an outer part 214. Inside the piston there is a compressible medium 215 and an incompressible medium 219. The pressure within the piston is regulated by a piston arrangement that is actuated directly by the pressure in chamber 216. The bottom piston 148 connected to the pressurized chamber 216 is attached to the piston rod 217, and the other side piston 149 is attached and connected to the medium of the piston 222. The piston rod 217 is guided by a slide bearing 218; other types of bearings may also be used (not shown). The pistons on both sides of the piston rod 217 are
Can have different diameters. That is, the cylinder 221 in which the piston rod 217 moves can even be replaced by two chambers of the type of the invention. Thereby, the piston and/or the piston is also of the type according to the invention. Sealing edge 220. Piston rod 224. Distance di between piston 148 and orifice 223
FIG. 112C shows the piston of FIG. 112A at the end of its stroke while there is still high pressure within chamber 216. Sealing edge 220'. The load adjustment means 148' have different distances from the orifice 223 towards the chamber. Pistons 148' and 149' are shown positioned at a greater distance from orifice 223: d2 than in Figure 112B.

Figures 113A, B, C show the combination of a pump with a pressurized chamber with elastically deformable walls with different areas of cross-section and a piston with a fixed geometry. For example, in a housing such as a cylinder with fixed geometric dimensions, an expandable chamber is disposed that can be expanded by a medium (incompressible and/or compressible medium). It is also possible to avoid the housing. The inflatable wall may, for example, comprise a liner fiber cover composite or add an impermeable skin. The angle of the sealing surface of the piston is slightly larger than the comparative angle of the chamber wall with respect to the axis parallel to the movement. said angle and the fact that the instantaneous deformation of the wall by the piston occurs with a slight delay (e.g. a viscous incompressible medium in the wall of the chamber and/or a This difference between (by having the right toning of the load adjustment means) provides a sealing edge and its to the central axis of the chamber during movement between the two piston and/or chamber positions. Distance may vary. This provides a change in cross-sectional area during the stroke, thereby providing a designable operating force. However, the cross section of the piston in the direction of movement may also be at an equal or negative angle to the angle of the chamber wall. In these cases, the "tip" of the piston should be rounded. In such cases, it may be more difficult to vary the cross-sectional area and thereby provide a programmable actuation force. The walls of the chamber may be provided with all the previously shown load adjustment means shown in FIG. 112B and, if necessary, shape adjustment means. The speed of the piston within the chamber can affect the seal.

FIG. 113A shows piston 230 in four positions of the piston within chamber 231.
The perimeter of the inflatable wall of the housing 234 has fixed geometric dimensions. Within the wall 234 is a compressible medium 232 and an incompressible medium 233. There may be a valve arrangement for inflating the wall (not shown). The shape of the piston on the non-pressurized side is just one example of the sealing edge principle. The distance between the end of the stroke and the seal edge at the beginning of the stroke in the cross section shown is approximately 39%. The shape of the longitudinal section may differ from that shown.

Figure 113B shows the piston after the start of the stroke. The distance from the sealing edge 235 and the central axis 236 is z1. The angle between the piston sealing edge 235 and the central axis 236 of the chamber is II. The angle between the wall of the chamber and the central axis 236 is v.

Angle v is less than angle λ. The sealing edge 235 is arranged so that the angle v is the same magnitude as the angle λ.
Other embodiments of the piston are not shown.

113C shows the piston during a stroke. The distance from sealing edge 235 and central axis 236 is z2, which is less than z1.
113D shows the piston near the end of the stroke. The distance from the sealing edge 235 and central axis 236 is z3, which is less than z2.

Figure 114 shows the combination of chamber walls and pistons with variable geometry that adapt to each other during the pump stroke and allow continuous sealing. The chamber of Figure 13A has only an incompressible medium 237 and a piston 222 at the beginning of the stroke, but the piston 222'' is shown just before the end of the stroke. All embodiments can also be used here. Correct selection of the speed of the piston and the viscosity of the medium 237 can have a positive influence on the operation. The longitudinal cross-sectional shape of the chamber shown in FIG. It may be different.

653 Description of the Preferred Embodiments Figure 201 A shows a longitudinal cross section of a non-moving, non-pressurized piston 5 in a first longitudinal position of a non-pressurized chamber 1 having a circular cross section with a constant radius. The piston 5 may have a production size approximately equal to the diameter of the chamber 1 in this first longitudinal position. The piston 5* is shown when pressurized to a pressure level. The pressure in the piston 5* creates a constant contact length.

Fig. 201B shows the contact pressure of the piston 5* of Fig. 201 A. The piston 5* can jam in this longitudinal position.
FIG. 202A shows a longitudinal cross section of a non-moving non-pressurized piston 5 in a first longitudinal position and the piston 5' in a second longitudinal position of a non-pressurized chamber 1 having a circular cross section with a constant radius in both the first and second longitudinal positions. The piston 5 may have a production size approximately equal to the diameter of the chamber 1 in this first longitudinal position. The piston 5' shows the piston 5 non-pressurized positioned within the small cross section in the second longitudinal position.

Fig. 202B shows the contact pressure of the piston 5' on the wall of the chamber in a second longitudinal position. The piston 5' can jam in this longitudinal position.
FIG. 202C shows a longitudinal cross section of a non-moving non-pressurized piston 5 in a first longitudinal position and a longitudinal cross section of the piston 5' in a second position of the non-pressurized chamber 1 having a circular cross section with a constant radius in the first and second longitudinal positions. The piston 5 may have a production size approximately equal to the diameter of the chamber 1 in this first longitudinal position. The piston 5'* shows the piston 5 pressurized to the same level as in FIG. 1A and positioned in a smaller cross section in the second longitudinal position.

Fig. 202D shows the contact pressure of the piston 5'* on the wall of the chamber in the second longitudinal position. The piston 5'* jams in this longitudinal position and the friction force may be 72 kg.
FIG. 203A shows the piston 5 of FIG. 201A and the deformed piston 5"* when pressurized to the same pressure level as the piston 5* of FIG. 201A. The deformation is caused by the pressure in the chamber 1* when the piston has no means of limiting its extension primarily in the meridian direction (the length of the chamber).

FIG. 203B shows the contact pressure. The piston 5"* may jam at this longitudinal position.
FIG. 204A shows a longitudinal section of the piston 15 in a second longitudinal position of the non-pressurized chamber 10 with a circular cross section. The piston 15 can have a production size approximately equal to the diameter of the chamber 10 in this second longitudinal position. The piston 15'* shows a deformed piston 15 pressurized to a certain level. This deformation is due to the fact that the Young's modulus in the hoop direction (cross-sectional plane of the chamber) is lower than that in the meridian direction (longitudinal direction of the chamber). - FIG. 204B shows the contact pressure on the wall of the piston 15'*. This results in a suitable friction force (4.2 kg) and a suitable seal.

FIG. 204C shows a longitudinal cross-section of piston 15 in a second longitudinal position (production size) of non-pressurized chamber 10, whereby when 15"* is pressurized in the first longitudinal position, piston 15"* can have the same pressure as when piston 15'* is located in the second longitudinal position of chamber 10 (FIG. 4A).
In addition, the deformation in the hoop direction and the meridian direction is also different.

FIG. 204D shows the contact pressure on the wall of the piston 15"*, which provides adequate friction (0.7 kg) and a suitable seal.
Thus, within the limits of the cross-sectional diameter selected in this experiment, it is possible to achieve a sealed movement of a piston containing an elastically deformable container from a smaller cross-sectional area to a larger cross-sectional area while having the same internal pressure.

Figure 205 A shows a longitudinal section of the piston 15 (production size) and piston 15'* in a second longitudinal position of the non-pressurized chamber 10. The piston 15'* shows the deformed structure of the piston 15 when it is pressurized. The pistons 15, 15'* are attached at their lower ends to an imaginary pneumatic piston rod to prevent piston movement during application of chamber pressure.

FIG. 205B shows the contact pressure of the piston 15'* of FIG. 205A, which is sufficient to allow movement (friction force 4.2 kg) and is suitable for sealing.
FIG. 205C shows a longitudinal cross section of piston 15 (production size) and 15″* pressurized and deformed by the chamber pressure in a second longitudinal position of pressurized chamber 10*. Pistons 15, 15′* are attached at their lower ends to an imaginary piston rod.

Instructions to Prevent Piston Movement During Application of Chamber Pressure The deformed piston 15''* is approximately twice as long as the undeformed piston 15.
Figure 205D shows the contact pressure of the piston 15"* of Figure 205C. This is sufficient to allow movement (3.2 kg of friction force) and is suitable for sealing.

Thus, if a piston consisting of a pressurized elastically deformable container is subjected to a chamber pressure, it can be similarly sealed, at least at the longitudinal position where the cross-sectional area is smallest. The elongation of the chamber due to the applied force may be large and may need to be limited.

Figures 206-209 address the limitations of the piston skin extension, which results in a contact area small enough to allow for a proper seal and a frictional force low enough to allow movement of the piston. can be done. This includes the restriction of longitudinal extension and movement from a second longitudinal position of the chamber to a first longitudinal position when the container may or may not be subjected to pressure within the chamber. When moving in the opposite direction, it can be inflated laterally, and in particular when moving in the opposite direction, it can be deflated.

The longitudinal extension of the wall of the container piston can be limited in several ways. This may be done by reinforcing the walls of the container, for example by using textile and/or fiber reinforcement. It can also be carried out inside the chamber of the container where the expansion body is placed with limited expansion while connected to the wall of the container. Other methods can be used, such as pressure management in a chamber between the two walls of the container, pressure management in the space above the container, etc. It is also possible to arrange the reinforcement on the outside of the piston.

The expansion behavior of the container wall may depend on the type of expansion restriction used. Furthermore, the retention of the piston moving on the piston rod while expanding may be guided by mechanical stops. The position of such stops may depend on the piston-chamber combination used. This also applies when guiding the container onto the piston rod while expanding and/or exposed to external forces.

All types of fluids can be used: combinations of compressible and incompressible media, only compressible media, or only incompressible media.
The change in the size of the container can be quite large, from the smallest cross-sectional area expanded with the largest cross-sectional area, having a manufacturing size, so that the chamber in the container and the first enclosed space in the piston rod, for example, communication may be required. The first enclosed space can also be pressurized during changes in the volume of the chamber of the container in order to maintain the pressure within the chamber. Pressure management of at least the first confined space may be required.

FIG. 206A shows a longitudinal section of a chamber 186 having a concave wall 185 and an expandable piston including a container 208 in a first longitudinal position within the chamber 186 and the same 208' in a second longitudinal position within the chamber 186. The container 208' shows its size when pressurized, which is approximately its production size, and includes a fabric reinforced 189 in the skin 188 of the wall 187.
During the stroke, starting from the second longitudinal position of the chamber 186, the wall 187 of the container expands until a stop device (which may be the textile reinforcement 189 and/or a mechanical stop 196 outside the container 208 and/or another stop device) that stops the movement during the stroke. Thus, an expansion of the container 208 occurs. Depending on the pressure in the chamber 186, a longitudinal expansion of the wall of the container may still occur due to the pressure in the chamber 186. However, the first main function of the textile reinforcement is to limit this longitudinal expansion of the wall 187 of the container 208. It results in a small contact area 198. The second main function of the textile reinforcement 189 is to allow contraction when the container is moving to the second longitudinal position (and vice versa if expansion is required). During the stroke, the pressure in the container 208, 208' may remain constant. This pressure depends on the change in the volume of the container 208, 208' and therefore on the change in the perimeter of the cross section of the chamber 186 during the stroke. It is also possible that the pressure may vary during the stroke, with or without depending on the pressure in chamber 186.

FIG. 206B shows a first embodiment of expansion piston 208 in a first longitudinal position of chamber 186. The walls 187 of the container are formed by a skin 188 of a flexible material, for example of the rubber type, with textile reinforcements 189 allowing expansion and contraction. The orientation of the fiber reinforcement relative to the central axis 184 (=braiding angle) differs from 54° 44'. The change in size of the piston during the stroke does not necessarily result in the same shape as depicted. Due to expansion, the wall thickness of the container may be less than the thickness of the container produced when placed in the second longitudinal position of chamber 186. An impermeable layer 190 may be present inside the wall 187. It is tightly squeezed into the top cap 191 and the bottom cap 192 of the container 208, 208'. Details of the cap are not shown and all kinds of assembly methods can be used. These can accommodate changes in the wall thickness of the container. Both caps 191, 192 can translate and/or rotate across the piston rod 195. These operations may be performed by various devices, such as, for example, various types of bearings not shown. The cap 191 on the top of the container can be moved upwardly and downwardly. A stop 196 on piston rod 195 outside container 208 limits upward movement of container 208. The lower cap 192 can only move downwards as the stop 197 prevents upward movement; this embodiment is used in piston-chamber devices that have pressure in the chamber 186 below the piston. it is conceivable that. For other types of pumps, such as dual-acting pumps, vacuum pumps, etc., other stop arrangements are possible and depend only on design specifications. Other arrangements may occur to enable and/or limit movement of the piston relative to the piston rod. Adjustment of the sealing force may include a combination of an incompressible fluid 205 and a compressible fluid 206 (both are possible alone) within the container, while the chamber 209 of the container is controlled by a spring force within the piston rod 195. It may communicate with a second chamber 210 that includes the actuation piston 126. Fluid can flow freely through the hole 201 through the wall 207 of the piston rod. The second chamber may be in communication with the third chamber (see FIG. 12), while the pressure within the container may also depend on the pressure within chamber 186. The container may be expandable through piston rod 195 and/or by communicating with chamber 186. O-rings or similar 202, 203 on the upper and lower caps seal the caps 191, 192 to the piston rod, respectively. Cap 204 is shown as an assembly threaded onto the end of piston rod 195 to tighten said piston rod. Similar stops can be placed at other locations on the piston rod depending on the required movement of the container wall. Contact area 198 between the container wall and the chamber wall.

FIG 206C shows the piston of FIG 206B in a second longitudinal position of the chamber. The top cap 191 has been moved a distance a' from the stop 196. The spring-actuated valve piston 126 has been moved a distance b'. The bottom cap 192 is shown adjacent to the stop 197, in this case there is pressure in the chamber 186 below the piston than the chamber 186' is forced against the stop 197. There is a compressible fluid 206' and an incompressible fluid 205'.

FIG. 206D is a three-dimensional view showing a reinforcing matrix of fibrous material that allows elastic expansion and contraction of the walls of the containers 208 , 208 ′ as they move confined within the chamber 186 .
The woven material may be elastic and may be laid in separate layers from each other. These layers may also be woven together. The angle between the two layers may differ from 54°44'. If the type and thickness of the material is the same for all layers and the number of layers is equal, the expansion and contraction of the container wall may be equal in the XYZ directions while the seam size in each direction is equal. When the seams ss, tt are stretched, they become larger in each direction of the matrix, respectively, and when they are contracted, they become smaller. Since the material of the thread may be elastic, another device to stop the expansion may be required, such as a mechanical stop. This may be a mechanical stop shown on the chamber wall and/or on the piston rod, as shown in Figure 206B.

Figure 206E is a three-dimensional view showing the reinforcement matrix of Figure 206D expanded. The seams ss' and tt' are larger than the seams ss and tt. As a result of the contraction, the matrix shown in Figure 206D may be motorized.

FIG. 206F is a three-dimensional view showing a reinforcing matrix of textile materials made of inelastic yarns (but elastically bendable) and lying in separate layers from each other or knitted together. Expansion is possible due to the extra length of each loop 700 that is available when the vessel is at production size and is also pressurized when placed in the second longitudinal position of the chamber. Ru. Seams in each direction ss, tt can limit the maximum expansion of the walls 187 of the container 217 if the container walls are expanding non-elastic materials. For example, a stop 196 may be required to stop the container 217 from moving over the piston rod 195, so that a seal remains. The absence of such a stop 196 may give the possibility of forming a valve.

FIG. 206G is a three-dimensional view showing the reinforcement matrix of FIG. 206F unfolded. The matrix shown in FIG. 206F can be motorized as a result of the stitches ss" and tt" contracting larger than the stitches ss" and tt".

Figure 206H shows three stages I, II and III of the manufacturing process of a piston containing an elastically deformable container. Positioned above the rod 400 is a rubber manchette 401, above which is positioned a reinforced manchette 402, for example, in FIGS. 406E-G. As previously mentioned, another rubber cuff is placed. One or more caps 404 can be placed between the machete 401 and the rod 404. Everything can slide on the rod 400. Rod 400 may be hollow and connected to a high pressure steam source. Stage II: Pressurized steam may enter the cavity 408 of the oven 406 by an outlet 405 that may be located at the end of the rod. Cut part of complete rubber/forced manchette 407 and rod 400
can be transported into the cave 408. It is better to close the cave than to inject pressurized steam into the cave. including attaching the walls of the container to the cap 404;
Vulcanization may occur. The cuff may take the form of a curve. After vulcanization, open a cave and push out a container larger than production size (III). Several methods can be used to manufacture other pistons using the piston's vulcanization time. Expansion of the rubber manchette 407 (complete: including textile reinforcement) may occur prior to vulcanization. The rod 400 may be divided upwardly into several sections, each section approximately equal to the height of the container at its manufacturing size. Each rod can be removed from the main rod before entering the cave. And/or there may be several cavities at the end of the production supply line, each stand being able to receive a complete manchette 407 and vulcanize it. This can be archived by means of cavities that rotate and/or translate to and from the ends of the production supply line. It is also possible that multiple vulcanization cavities may be incorporated into the production supply line.

Figure 207A shows a longitudinal section of a chamber 186 with a concave wall 185 and an expandable piston including a container 217 in a first longitudinal position of the chamber and the same 217' in a second longitudinal position. shows. Container 217' is shown pressurized to approximately its production size.

FIG. 207B shows the expansion piston 217 in a first longitudinal position of the chamber. The wall 218 of the vessel is formed by a skin 216 of elastic material, for example rubber type, with a fiber reinforcement 219 by trellis effect that allows the expansion of the vessel wall 218. The orientation of the fibers relative to the central axis 184 (= braid angle) may be different from 54° 44'. The contact area 211 between the wall 218 of the vessel 217 and the wall 185 of the chamber 186. Due to the expansion, the thickness of the vessel wall may be smaller, but not necessarily significantly different from the thickness of the vessel produced when placed in the second longitudinal position. There may be an impermeable layer 190 on the inside of the wall 187. It may be tightly pressed to the top cap 191 and the bottom cap 192 of the vessel 217, 217'. Details of said caps are not shown, any kind of assembly method can be used. These can adapt to the change in the thickness of the vessel wall. Both caps 191, 192 can translate and/or rotate over the piston rod 195. These movements can be achieved by various methods, such as, for example, by various types of bearings, not shown. The top cap 191 can move up and down until a stop 214 limits this movement. The bottom cap 192 can only move downwards, as a stop 197 prevents upward movement. This embodiment is considered to be used for piston-chamber devices with pressure in the chamber 186 below the piston. In other types of pumps, e.g., double acting pumps, vacuum pumps, etc., other stop arrangements are possible and depend only on the design specifications. Other arrangements for allowing and/or limiting the movement of the piston relative to the piston rod may occur.

During the stroke, the pressure in the container 217, 217' may remain constant. Also, the pressure may vary during the stroke. The timing of the sealing force may include a combination of incompressible fluid 205 and compressible fluid 206 (both may be alone) in the container, while the chamber 215 of the container 217, 217' may communicate with a second chamber 210 containing a spring force actuated piston 126 in a piston rod 195. Fluid may be free to flow through the hole 201 through the wall 207 of the piston rod. The second chamber may communicate with a third chamber (see FIG. 210), while the pressure in the container may also depend on the pressure in the chamber 186. The container may be expandable through the piston rod 195 and/or by communicating with the chamber 186. O in the upper cap and the lower cap may be connected to the piston rod 195.
Rings or the like 202, 203 seal the caps 191, 192, respectively, to the piston rods. Cap 204 is shown as an assembly threaded onto the end of piston rod 195, clamping said piston rod.

207C shows the piston of FIG. 207B in a second longitudinal position of chamber 186. The contact area 211' is small. Cap 191 is moved a distance c' from stop 216. Spring force actuated valve piston 126 has moved over a distance d'. Bottom cap 192 is shown closer to stop 197 when there is pressure in chamber 186 than when 192 is pressed against stop 197. A compressible fluid 206' and an incompressible fluid 205' that can change the volume within the container.

Figures 208A, B, C deal with a piston construction that may be identical to Figures 207A, B, C, with the exception that the rebar may include any type of rebar means that may be bendable, and may be in a pattern of rebar "pillars" that do not cross each other. This pattern may be parallel to the central axis 184 of the chamber 186, or one in which a portion of the reinforcing means may lie in a plane that passes through the central axis 184.

FIG. 208A shows an expandable piston with a container 228 in a first longitudinal position of the chamber 186 and the same 228' in a second longitudinal position of the chamber 186, where it is pressurized and where it has been depressurized to its production size.

FIG. 208B shows the container 228 in a first longitudinal position in the chamber 186 .
The wall 221 of the container comprises elastic material 222, 224 and reinforcing means 223, e.g. fibres. An impermeable layer 226 may be present. The contact area between the container 228 and the wall 185 of the chamber 186.

FIG. 208C shows the container 228' in a second longitudinal position of the chamber 186.
Contact area 225' may be slightly larger than that of contact area 225. Top cap 191 has moved e' from stop 214.

FIG. 208D shows a top view of pistons 228 and 228' having reinforcing means 223 and 223'' at first and second longitudinal positions of chamber 186, respectively.
FIG. 208E shows a top view of a piston similar to the one of 228 and 228', respectively, with alternative embodiments of reinforcing means 229 and 229', respectively, at first and second longitudinal positions of chamber 186. Part of the reinforcing means does not lie in a plane passing through central longitudinal axis 184 of chamber 186. FIG. 208F shows a top view of a piston with reinforcing means 227 and 227' in the walls of the vessel in a plane not passing through central axis 184 of chamber 186. During the stroke, the walls of the vessel rotate around central axis 184.

FIG. 208G shows diagrammatically how fiber 402 is attached to cavity 431 in cap 430. This can be achieved by rotating the cap and fiber about a central axis 433, where each fiber can have its own speed, while fiber 432 is forced towards and within cavity 431.

Fig. 209A shows a longitudinal section of the chamber 186 with a convex wall 185 and an expandable piston containing a reservoir 258 and the same 258' at the end of the stroke. A second longitudinal position of the pressurized reservoir 258'.

FIG. 209B shows a longitudinal section of a piston 258 having a reinforced skin with a plurality of at least elastically deformable support members 254 rotatably fixed to a common member 255 connected to the skin 252 of said pistons 258, 258'. Show the face. These members are tensioned and have a certain maximum extension length, depending on the hardness of the material. This limited length limits the extension of the piston skin 252. The common member 255 can slide on the piston rod 195 using sliding means 256. The remainder is of a structure comparable to that of the pistons 208, 208'. Contact area253.

Fig. 209C shows a longitudinal cross section of piston 258'. Contact area 253'.
Figures 210-212 deal with the management of pressure in the container. Pressure management of a piston with an expandable container with elastically deformable walls is an important part of the piston-chamber design. Pressure management is concerned with maintaining the pressure in the container to keep the seal at the right level. This means during each stroke the volume of the container changes. Also, in the long term, if the container leaks, the pressure in the container can decrease and affect the seal. If the volume changes during the stroke and/or the flow of liquid into and/or out of the container itself (expansion), the solution can be the flow of liquid into and/or out of the container.

The change in the volume of the container is balanced by the change in the volume of the first sealed space, which communicates with the container, for example, through a hole in the piston rod. At the same time, the pressure may be balanced, which may be done by a spring-force actuated piston, which may be positioned in the first sealed space. The spring force can be generated by a spring or a pressurized sealed space, for example, a second sealed space that communicates with the first sealed space by a pair of pistons. The transmission of any kind of force can be performed by each of the pistons, for example, when a fluid moves from the first sealed space into the container,
The second enclosed space and the piston pair may be arranged, for example, so that when the piston pair moves towards the first enclosed space, the force on the piston in the second enclosed space decreases, while the force on the piston in the first enclosed space is equal. This corresponds well with p. V = constant in the second enclosed space. Also, the regulation of the pressure in the chamber of the container during the entire stroke or part of it can be done by communication of the chamber with the chamber of the container. This has already been described in WO00/65235 and WO00/70227.

The reservoir can be inflated through a valve in the piston and/or a handle on the piston rod.
The valve may be a check valve or an expansion valve, for example a Schrader valve. The container may be inflated through a valve communicating with the chamber. If an expansion valve is used, a Schrader valve is preferred as it is safe to avoid leakage and has the ability to control any type of fluid. To allow the expansion, a valve actuator may be required, for example the actuators disclosed in WO99/26002 or U.S. Pat. No. 5,094,263. WO99/26002
This valve actuator has the advantage that it requires very low inflation forces and is therefore very practical for manual inflation, and when combined with a spring-loaded valve, it closes automatically when an equal pressure level is reached.

Where the flow of pressurised volume from the enclosed space to the vessel is substantial, and vice versa, it is preferred to have a pressure/volume source with a volume larger than the volume of the enclosed space and a pressure level equal to, lower than or higher than the pressure in the vessel. In the aforementioned cases, the volume of the pressure source can be small compared to a pressure source with an equivalent pressure level to the vessel.

If the pressure level of the pressure source is higher than the pressure level of the vessel, it may be necessary to steer the flow between the pressure/volume source and the vessel during the stroke with a valve. These valves may have a spring force actuated core pin, which may be actuated. The actuator can open or close the valve which constantly changes the flow. For example, there are similar structures used to inflate a vessel due to a pressure drop caused by a leak (see next page). Other types of valves and valve steering solutions are possible. This is also the method below.

Maintaining pressure within a vessel at a constant level.
Having a valve in communication with the vessel may allow automatic inflation of the vessel if the pressure in the vessel is lower than the pressure in the vessel. If this is not possible, such a high pressure in the chamber may be temporarily created by closing the outlet valve of the chamber near the second longitudinal position of the vessel in the chamber. This closing and opening may be done manually, for example by a pedal, which opens a channel that communicates with the space between the valve actuator (WO99/26002) and, for example, a Schrader valve. When open, the valve actuator moves but lacks the force to press the spring-force actuated core pin of the valve and therefore the Schrader valve may not open, thus the chamber is closed and any high pressure may build up to allow inflation of the vessel. Once the channel is closed, the actuator functions as disclosed in WO99/26002. The operator can check the pressure in the vessel by a pressure gauge, for example a manometer. This opening and closing of the outlet valve may also be done automatically. This may be done by any kind of means, which initiates the closing of the outlet by any kind of signal as a result of the pressure measurement being lower than a predetermined value.

The automatic expansion of the container to a certain predefined value can be achieved by a combination of a valve communicating with the chamber, for example a release valve of the container, which is released, for example, to a space or chamber above the container at a certain predefined pressure value. Another option is that the valve actuator of WO99/26002 can be initially opened when a predefined value of pressure is reached, for example by combining it with a spring. Another option is that the opening of the valve actuator can be closed, for example by a spring-force actuated piston or cap, when the pressure exceeds a predefined value. Or by combining the piston 292 of FIG. 211E with a means, the piston opens the channel 297 when a certain pressure is reached (not shown).

Figure 210A shows a piston-chamber system comprising a piston with a container 208, 208' and a chamber 186 having a central axis 184 according to Figures 206A-C. The expansion and pressure management described herein can also be used with other pistons, including vessels. Container 208, 208' can be inflated via valve 241 on handle 240 and/or valve 242 on piston rod 195. If a handle is not used, but a rotating shaft is used, for example, it may be hollow, communicating with a Schrader valve or the like. Valve 241 may be an expansion valve, such as a Schrader valve, including bushing 244 and bushing 244.

The valve in the valve core 245 piston rod 195 may be a check valve with a flexible piston 126. The chamber between the check valve 242 and the chamber 209 of the container 208, 208 was previously described as the "second" chamber 210. A manometer 250 allows the pressure in the container to be controlled. Details are not shown. It would also be possible to use this manometer to control the pressure in the chamber 186. It is also possible that the chamber 209 of the container 208, 208' has a discharge valve (not shown) that can be adjusted to a predetermined pressure value. The discharged fluid can be directed to the chamber 209 and/or to the space 251.

FIG. 210B shows an alternative option for expansion valve 241. Instead of the expansion valve 241 in the handle 240, there may only be a bush 244 without a valve core 245, which allows connection to a pressure source.

FIG. 210C shows details of the bearing 246 of the rod 247 of the check valve 126. Bearing 246 includes a longitudinal duct 249 that allows passage of fluid around rod 247. Spring 248 allows pressure on the fluid within second chamber 210. Stop 249.

210D shows details of the flexible piston 126 of the check valve 242. A spring 248 maintains pressure on the piston 126.
FIG. 210E shows a pressure source 451 that may have a pressure that exceeds the pressure level of the container. For example, an inlet valve 452 (configuration 459 shown is similar to the one in FIG. 211E (292, 297)) with a valve actuator 453 and an outlet valve 454 (configuration 451 shown is similar to the one in FIG. 211E (292, 297)) with a valve actuator 455. Space 460 is connected to chamber 457 and space 462 is connected to chamber 458. Valves 452 and 454 may be attached to a piston rod 456, which may be divided upwardly into two chambers 457 and 458.

FIG. 210F shows the structure of FIG. 210E, where two black boxes are each shown containing a valve arrangement that can be steered by an external signal. Steering 415 can receive pressure signals 416 and 417 from inside the piston at different longitudinal positions of the chamber, respectively. The steering 415 is connected to the actuator 422 of the outlet valve device 420, respectively.
and signals 418 and 419 to the actuator 423 of the inlet valve device 421. This valve and valve steering configuration may be similar to that shown in FIG. 211F.

FIG. 211 A shows a piston-chamber system comprising a piston with a container 248, 248', the central part of which is identical to the container 208, 208', and a chamber 186 with a central axis 184 according to FIG. 206A-C. The expansion and pressure management described herein can also be used for other pistons including a container. The container 248, 248' can be expanded through a valve communicating with the chamber 186. This valve can be a check valve 242 according to FIG. 210A, D or it can be an expansion valve, preferably a Schrader valve 260. The first enclosed space 210 communicates with the chamber 209 in the container by means of a hole 201, and the first enclosed space 210 communicates through the piston device with a second enclosed space 243, which can be expanded through an expansion valve, such as a Schrader valve 241, which can be arranged in the handle 240 for example. The valve has a core pin 245. If a handle is not used, but for example a rotating shaft is used, which may be hollow, a Schrader valve may be in communication with this channel (not pulled). The Schrader valve 260 has a valve actuator 261 according to WO 99/26002. A foot 262 of the chamber 186 is connected to an outlet valve 263.
, for example a Schrader valve, which may be provided with another valve actuator 261 according to WO 99/26002. To manually control the outlet valve 263, the foot 262 may be provided with a pedal 265 which can be rotated an angle a around an axle 264 on the foot 262. The pedal 265 is connected to a piston rod 267 by an axle 266 in a non-circular hole 275 in the top of the pedal 265. The foot 262 has an inlet valve 269 (untensioned) for the chamber 186. A (schematically drawn) spring 276 holds the pedal 265 in its initial position 277, where the outlet valve remains open. If the outlet valve remains closed, the actuated position 277' of the pedal 265
. Exit channel 268.

FIG. 211B shows details of communication between the first sealed space 210 and the second sealed space 243 by the pair of pistons 242, 270. Piston rods 271 of the pair of pistons are guided by bearings 246. A longitudinal duct 249 of the bearing 246 allows fluid transport from the space between the bearing 246 and the pistons 242 and 270. A spring 248 may also be present. The piston rod 195 of the piston-shaped container 248, 248' has an inner wall 194. Pistons 242,270 are sealed onto inner wall 194.

FIG. 211C shows an alternative wall 273 of the piston rod 272 of the piston-shaped vessel 248, 248' having an angle β with the central axis 184 of the chamber 186. Piston 274 is depicted schematically and can accommodate varying cross-sectional areas inside piston rod 272.

FIG. 211D shows piston 248' to which housing 280 is assembled. The housing includes a Schrader valve 260 having a core pin 245. A valve actuator 261 is shown pushing core pin 261 while fluid enters valve 260 via channels 286, 287, 288, and 289. When core pin 245 is not pushed, piston ring 279 can seal against wall 285 of inner cylinder 283. Inner cylinder 283 may be sealingly surrounded by seals 281 and 284 between housing 280 and cylinder 282. chamber 186.

FIG. 211E shows the configuration of outlet valve 263 with core pin 245, which is shown depressed by valve actuator 261. Fluid is directed through channels 304, 305, 306, and 307.
to an open valve. Inner cylinder 302 is sealingly enclosed between housing 301 and cylinder 303 by seals 281 and 284. A channel 297 having a central axis 296 is disposed through the wall of inner cylinder 302, the wall of cylinder 303, and the wall of housing 301. On the exterior of housing 301 is an opening 308 of channel 297 and a widened portion 309 which allows piston 292 to seal in closed position 292' with top 294.
The piston 292 may move in another channel 295, which may have the same central axis 296 as the channel 297. The piston 292 has a bearing 293 for a piston rod 267. The piston rod 267 may be connected to a pedal 265 (FIG. 211A) or other actuator (shown diagrammatically in FIG. 211E).

FIG. 211E' is processed after FIG. 218B.
FIG. 211F shows the piston 248' of FIG. 211D in addition to the arrangement 369 for controlling the outlet valve of FIG. 211E.
and an expansion arrangement 368. Here, the expansion mechanism 368 also includes a mechanism 370 for controlling the valve of FIG. 211E. This can be done to allow the valve to close when a predetermined pressure is reached and to open when it is below a predetermined value. The signal 360 is processed in a transducer 361 which gives a signal 362 to an actuator 363 which is actuating the piston 292 via an actuating means 364.

If the chamber has an operating pressure lower than a predetermined value of the pressure in the piston, the outlet valve 263
The arrangement 369 controlling the closing and opening of can be controlled by another actuator 363 via means 367 triggered by a signal 365 from the transducer 361. Measurements in the chamber that provide signals 371 to transducers 361 and/or 366 can automatically detect whether the actual pressure in the chamber is lower than the operating pressure of the piston. This may be particularly practical if the pressure in the piston is below a predetermined pressure.

FIG. 211G shows a schematic of a cap 312, 312' with a spring 310 connected to a housing 311 of a valve actuator 315. The spring 310 may keep the opening 314 tightly closed. The contact area 313 of the cap 312 with the cylinder 282 (FIG. 211D). When the force on the cap 312 from the chamber becomes greater, the cap may move to the position shown in FIG. 312' until there is an equality of the force on the cap by the medium in the chamber/medium. The spring 310 may determine the maximum value of the pressure pressing against the valve core pin 245. Schrader valve 260
FIG. 212 shows an elongated piston rod 320 having a pair of pistons 321 , 322 disposed at the end of the piston rod 323 which may move within bearings 324 .

Figures 213A, B, C show a pump combination of a pressurized chamber with an elastically deformable wall with different regions of cross-section and a piston with a fixed geometry. For example, within a housing, such as a cylinder with fixed geometric dimensions, an expandable chamber is disposed that is expandable by a fluid (incompressible and/or compressible fluid). It is also possible to avoid the housing. The inflatable wall may, for example, comprise a liner fiber cover composite or add an impermeable skin. The angle of the sealing surface of the piston is slightly larger than the comparative angle of the chamber wall with respect to the axis parallel to the movement. the angle;
The fact that the instantaneous deformation of the wall by the piston occurs with a slight delay (e.g., having a viscous incompressible fluid within the walls of the chamber, and/or a load adjustment similar to that shown for the piston) This difference between (by appropriate adjustment of the means) provides a sealing edge, the sealing distance of which may vary during movement between the two piston and/or chamber positions up to the central axis of the chamber. . This provides a change in cross-sectional area during the stroke, thereby providing a designable operating force. However, the cross section of the piston in the direction of movement may be equal to or at a negative angle to the angle of the chamber wall. In these cases, the "tip" of the piston may be rounded. In such cases, it may be more difficult to vary the cross-sectional area and thereby provide a programmable actuation force. The walls of the chamber can be provided with all the previously shown loading adjustment means shown in FIG. 212B and, if necessary, with shape adjustment means. The speed of the piston within the chamber can affect the seal.

FIG. 213A shows piston 230 in four positions of the piston within chamber 231.
Around an expandable wall of a housing 234 with fixed geometric dimensions. Within said wall 234 there is a compressible fluid 232 and an incompressible fluid 233. There may be a valve arrangement. Expansion of the wall (not shown). The piston shape on the non-pressurized side is only an example showing the principle of the sealing edge. The distance between the sealing edge at the end and start of the stroke in the cross section shown is about 39%. The shape of the longitudinal section may differ from that shown.

Figure 213B shows the piston after the start of the stroke. Distance from seal end
235 and the central axis 236 is z1. The angle II between the piston sealing edge 235 and the central axis
of the chamber 236. Angle v between the wall of the chamber and the central axis 236. Angle v is less than angle λ. The sealing edge 235 is positioned such that angle v is the same as angle λ. Other embodiments of the piston are not shown.

213C shows the piston during a stroke. The distance from the sealing edge 235 and the central axis 236 is z2, which is less than z1.
213D shows the piston near the end of the stroke. The distance from the sealing edge 235 and central axis 236 is z3, which is less than z2.

Figure 214 shows the combination of chamber walls and pistons with variable geometries from 2 to 28 that adapt to each other during the pump stroke and allow continuous sealing. It has its production size in the second longitudinal position of the chamber.

The chamber in FIG. 213 A is now the chamber in FIG. 213 A with only the incompressible medium 237 and the piston 385 at the beginning of the stroke, while the piston 385' is shown just before the end of the stroke. Also, all other embodiments of the piston, which may vary in dimensions, can be used here. The correct choice of the speed of the piston and the viscosity of the medium 237 can have a positive effect on the operation. The longitudinal cross-sectional shape of the chamber shown in FIG. 14 can also be different.

Figures 215A-F illustrate embodiments of chambers with different sized cross-sections having a constant perimeter size. This is another solution to the piston blockage problem cited in WO 00/70227. The piston according to claim 1 is characterized in that by means of skin reinforcement, parts of the wall of the container with different distances from the central axis of the chamber can be used in the longitudinal section of the chamber, e.g. may also work well in these particular chambers. Figure 208D is approximately parallel to the central axis of the chamber, where the reinforcement consists of, for example, elastic screws (Figures 206D, 206E), or those shown in the figure. For 206F and 206G, each size can be set individually. It is shown in the figure.

ここで、

cp = ｆ(x)の余弦重み付け平均値、
dp = 12(x)の正弦重み付け平均値、
p = 三角法の細かさの次数を表す。 209A, 209B may also work well. The piston can move unhindered in such chambers, either inelastically deformable or elastically deformable, whose manufacturing size is approximately the same as the circumferential length of the first longitudinal position of the chamber, and which has a reinforcement that allows contraction by high frictional forces, and jam in chambers with different circumferential sizes in cross section. If the braid angle of the reinforcement of the container is 54°44', the elastically deformable container becomes inelastically deformable, i.e., flexibly deformable, but does not jam in these chambers, since it can be bent. If the change between the two positions in the direction of movement of the area of the cross section of the piston and/or chamber is continuous, but still very large, and leakage occurs, it is advantageous to minimize the change in other parameters of the cross section. This can be illustrated, for example, by using a circular cross section (fixed shape). That is, the circumference of the circle is πD and the area of the circle is 1/4πD ² (D = diameter of the circle). That is, the reduction of D gives only a linear reduction in the circumference and a quadratic reduction in the area. It is also possible to maintain the perimeter, just reduce the area. Also, if the shape is fixed, e.g. circular, there is a certain minimum area. Advanced numerical calculations where the shape is a parameter can be done using the Fourier series expansion below. Pressurized chambers and/or
Alternatively, the cross section of the piston may have any shape, which may be defined by at least one curve. The curve is closed and has a 1:1 ratio for each coordinate function.
Each can be roughly defined by two unique modular parameterized Fourier series expansions.

here,

cp = cosine weighted average of f(x),
dp = sine-weighted average of 12(x),
p = the degree of trigonometric detail.

Figures 215A, 215E show examples of said curves by using different sets of parameters in the following formulas. In these examples, only two parameters are used. If more coefficients are used, it is possible to find optimized curves that meet other important requirements. For example, curve transitions with the maximum radius of the curve and/or, for example,
It is possible to find the maximum possible seal tension that does not exceed a certain maximum under a given prism. As an example, Figure 215F shows optimized convex and non-convex curves used for possible deformations of a bounded region in a plane, with the constraint that the length of the boundary curve is fixed and its numerical curvature is minimized. Using the starting region and the starting boundary length, it is possible to calculate the minimum possible curvature for the desired target region.

The pistons shown in longitudinal section through their chambers are primarily drawn when the boundary curve of the cross section is circular. That is, if the chamber has a non-circular cross section, e.g., as in Figures 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 Figure 1A). One feature of these curves is that when a line is drawn from the mathematical poles in the cross section,
It must intersect the curve at least once. The curve is symmetrical towards a line in the cross-sectional plane and can be generated by a subsequent single Fourier series expansion. Pistons or chambers are easier to manufacture if:

ここで、

cp = ｆ（ｘ）の重み付き平均値
p = 三角法の細かさの次数を表す. .
線が数学的極から引かれるとき、線は常に1回だけ曲線と交わる。 A curve in a cross section is symmetrical about a line in the cross-sectional plane that passes through the mathematical pole. Such a regular curve can be approximately defined by a single Fourier series expansion.

here,

cp = weighted average of f(x)
p = the degree of trigonometric precision.
When a line is drawn from a mathematical pole, the line will always intersect the curve exactly once.

ここで、

cp = ｆ（ｘ）の重み付き平均値
p = 三角法の細かさの次数を表す. .

極座標におけるこの断面は、ほぼ以下のように表される。
. 計算式:

ここで、

ここで、
r = 活性ピンの円形断面の"花弁"の限界、
ro = 活性ピンの軸の周りの円形断面の半径、
a = "花弁"の長さのスケールファクター
r_max = r₀ + a
m = 「花弁」幅の定義のためのパラメーター
n =「花弁」の数の定義のためのパラメーター
φ = 曲線を境界する角度
注入口は、ピストン手段のシール部の性質のため、ストロークの端部の近くに位置決めされる。 The particular formed sector of the cross-section of the chamber and/or piston may be approximately defined by the following equation:

here,

cp = weighted average value of f(x)
p = represents the degree of fineness of trigonometry.

This cross section in polar coordinates can be expressed approximately as follows.
. a formula:

here,

here,
r = "petal" limit of the circular cross section of the active pin,
ro = radius of the circular section around the axis of the active pin,
a = "petal" length scale factor
r _max = r ₀ + a
m = parameter for the definition of the "petal" width
n = parameter for the definition of the number of "petals" φ = angle bounding the curve The inlet is positioned close to the end of the stroke due to the nature of the sealing part of the piston means.

These specific chambers are formed by injection molding and also by pressing, for example, when an aluminum sheet is forced into a tool cavity and heated by air pressure, or by using also tool movements, so-called It can be manufactured by using superplastic forming methods.

Figure 215A shows a series of cross-sections of the chamber. In this region, the area decreases at a given step, but the perimeter remains constant, and these are defined by two unique modular parameter Fourier series expansions, one for each coordinate function. In the upper left,
There is a cross section that is the starting cross section of said series. The set of parameters used is shown at the bottom of the figure. This series shows a decreasing area of the cross section. The bold numbers in the figure indicate that the cross-sectional area of the different shapes is reduced, and the cross-sectional area of the corner is left as the size of the starting region.

The area of the shape on the right side of the bottom of the cross section is approximately 28% of the area on the left side of the top.
FIG. 215B shows a longitudinal section of chamber 162, the cross-sectional area of which varies with the remaining circumference along the central axis.

Piston 163. The chamber has parts of different cross-sectional areas of its cross section in wall sections 155, 156, 157, 158. Transitions 159, 160, 161 between said wall sections. Sections GG, HH
, II are shown. Section GG has a circular cross section, while section HH 152 has about 90-70% of the area of section GG.

FIG. 215C is shown as comparative cross-section GG 150 and cross-section H-H 152 of FIG. 207G and in dotted line. The area of cross section H-H is approximately 90 to 70% of the area of cross section G-G. 151 smoothed transitions. Also shown is the smallest part of the chamber, which has approximately 50% of the cross-sectional area of section G-G.

FIG. 215D shows cross section II of FIG. 207G and a dotted line as a comparative cross section GG. The area of cross section II is about 70% of the area of cross section GG. The transition 153 is smoothed. Also,
The smallest part of the chamber is also shown.

Figure 215E shows a series of cross sections of a chamber with constant perimeter while decreasing area in constant steps. These are defined by two unique modular parameter Fourier series expansions, one for each coordinate function. At the top left is the cross section that is the starting cross section for said series. The set of parameters used is shown at the bottom of the figure. While this series shows a decreasing area of cross sections, it is also possible to increase these areas by maintaining the circumference constant. The bold numbers in the figure indicate the decreasing cross sections of different shapes, with the cross sections at the corners being left as the size of the starting region. The size of the cross section at the bottom right is approximately 49% of the size of the starting region, and at the top left.

Figure 215F shows an optimized convex curve for a constant length of the boundary curve and the minimum possible curvature. The general formula for the minimum radius of curvature corresponding to the maximum curvature in the diagram shown in FIG. 7L is as follows.

yで特定された長さは、次の式で決定される。

The length specified by y is determined by the following formula:

ここで、
r = 最小曲率半径
L=境界長=定数。
A1 = 開始ドメイン領域A0の減少値

図203Dからの例として、半径30のディスクの面積および境界長に対応するドメイン領域Ao
= π(30)2および境界長L=60π=188.5。長さは一定であることが必要であるが、領域は指定される値A1まで減少する。所望の最終構成は、面積A1 = π (19/2)2 = 283.5 とする。ここで、境界曲線の可能な限り最小の曲率をもつ凸曲線は、次のようになる。

here,
r = minimum radius of curvature
L = boundary length = constant.
A1 = the reduction in the starting domain region A0

As an example from FIG. 203D, the domain area Ao corresponding to the area and boundary length of a disk of radius 30
= π(30)2 and boundary length L = 60π = 188.5. The length needs to remain constant, but the area is reduced to a specified value A1. The desired final configuration has area A1 = π (19/2)2 = 283.5. Now the convex curve with the smallest possible curvature of the boundary curve is:

r = 1.54
Kappa = 1/r = 0.65
x = 89.4
The curves in the diagram are not to scale, the diagram illustrates the principle only.

The curve can be further optimized by replacing the straight line with a curve that can improve the sealing to the wall of the piston.
FIG. 216 shows a piston combination including an elastically deformable container 372 moving within a chamber 375 within a cylinder wall 374 and a tapered wall 373 shown centered around a central axis 370, for example. The piston is suspended on at least one piston rod 371. The containers 372, 372' are shown in the second longitudinal position of said chamber (372') and in the first longitudinal position (372').

All the solutions disclosed in this specification can also be combined with piston types, where a chamber with a cross section having a constant perimeter can be a solution to the blockage problem.
Fig. 217A shows a convex chamber 380 in a wall 381. The "s" stands for stroke.

FIG. 217B shows a force-stroke diagram for the direction shown in FIG. 217A.
The curve shows the optimized change in force as the operator pumps with a stroke in which the fluid inlet is approximately at a first longitudinal position of the chamber and the outlet is approximately at a second longitudinal position of the chamber. The curve shows the maximum operating force approximately at the end of the pump stroke as a tangent.

FIG. 218A shows an example of a mobile power unit 390 , which is shown to be mobile by parachute 391 and wheels 392 .
FIG. 218B shows a mobile power unit 390 with a set of solar cells 393 and a motor 394 on top, as well as a water pump 395, and a compressor 396. A steering unit 397 is also shown.

FIG. 211E' shows an adaptation to the outlet valve shown in FIG. 211E. The piston rod 267 is connected to a second channel pin 8001. Said channel pin is attached to a guide channel 8002. The channel pin closes an equalization channel 8003. Said channel pin has a hole that allows flow through the channel 8003 when the piston rod 267 pushes the piston 292 in the opening 308 of the channel 297. Said equalization channel connects the channels 305, 306, 307 in the valve to an outflow chamber 8004. Said outflow chamber may be the outflow chamber of the valve. This configuration is
Used when the pressure increase in the inlet chamber of the valve is not sufficient to actuate the valve, low pressure from the outlet chamber of the valve can be used to trigger actuation of the valve.
507 Description of the Preferred Embodiments Fig. 301 shows a valve actuator in a clip-on valve connector to be connected to, for example, a Schrader valve. A piston 477 is 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 fastening means comprises a temporary thread 476. The housing also has a central axis 479 and a coupling portion 510.

Fig. 301A shows an enlarged detail of Fig. 301. The cylinder 470 has a cylinder wall 511 with a diameter that fits the piston ring 508 of the piston 477. Near the first end 492, the cylinder wall includes wall portions 475a, 475b, 476a with enlarged diameter, which contain flow passage portions 471, 472, 473 around the piston means 477, 508 when the core of the valve is fully opened. A flow from a pressure source to the valve can be established. The first end 492 of the cylinder 470 serves here as a stop for the movement of the actuation pin. The channel portions 473, 474 are part of the piston control means 476c. These parts can have several shapes depending on the manufacturing technique chosen, for example the channel portions 473, 474 as circular sector parts, the channel portion (507) as a cylinder made by injection molding, while the channel portion (507) can also have drilled holes. The channel parts 473 and 474 are considered to be "flow shapes";
The inclined expanding wall 475a has an angle τ with the central axis 479, typically between 1°<τ<12°, which is greater than 0° and less than 20°, with respect to the direction of the gaseous and/or liquid medium or media coming from the pressure source, respectively. The piston control means 476c has three grooves, each with a wall 476a and 476b. The wall 476a has an angle ω, typically between 6° and 12°, with respect to the direction of the gaseous and/or liquid medium or media coning from the pressure source. An alternative to the aforementioned channel portions 473 and 474 is a channel (507) where the piston control does not have a groove. In this alternative, a hole (507) beside the piston control device, parallel to the central axis 479, is formed in the channel portion 476c.
Connect 5b (shown as three holes with dotted lines) with the coupling hole.

Figure 301B shows section GG from Figure 301A, with channel portions 473 and 474 and stopper 492. An alternative channel portion (507) is sketched by a dotted line.
FIG. 302 shows a valve actuator in a universal clip-on valve connector having a housing 504, a sealing means comprising a first annular portion 482 and a second annular seal.

A portion 483 located in the direction of the central axis 486 of the joint 503 and coaxially with the central axis 486 of the joint. 1st
The annular seal portion 482 is closer to the opening 502 of the coupling portion than the second annular seal portion 483, and the diameter of the first annular seal portion 482 is larger than the diameter of the second annular seal portion 483. The coupling valve can be fixed by at least one “clip” (=ie temporary thread) 476. However, two clips 493 on opposite sides of each other are preferred. Tapered cone 501 near sealing surface 482 helps center the valve. The tapered cone has an angle ω with the central axis 486, which typically exceeds 45°. A separate cylinder sleeve 496 with cylinder wall 509 is shown and sealed. It is secured, for example, by a snap lock 497 on the wall of the housing 504. This is an economical way to allow negative sliding angles of the sloped expansion wall 512. Cylinder sleeve 496 is angled away from piston stop 495 so that piston ring 508 is not sealed there.

Fig. 302A shows the channel parts 480, 481 defined by the enlarged wall parts 487, 488 of the piston control means, respectively. The actuation pin is streamlined by the piston 484 and the piston rod 485. The wall part 487 has an angle κ with the central axis 486 seen in the direction of the medium coming from the pressure source, which is greater than 0° and less than 20° (usually with an interval between 6° and 12°). The stepped surface 498 of the wall of the housing 504 forms an airtight connection from the wall of the cylinder sleeve 496 to the cylinder 499. Of course, it is also possible to provide an airtight connection on the opposite side of the cylinder. At the bottom of the cylinder sleeve 496, an inclined enlarged wall part 512 is shown, which together with the piston ring 515 forms the channel part 471.

Fig. 302B shows section HH of Fig. 302A and a stop 495 for movement of the actuation pin. Also shown are wall portion 488 and channel portion 481.
Fig. 303 shows an actuation pin equivalent to that of Fig. 301, and also shows a piston 529. The piston rod 531 does not need to be sealed to the piston control. The valve actuator cylinder 536 is within the valve connector housing 532. The coupling 530 is also shown.

FIG. 303A shows a channel portion 533 with an extension 535 and a channel portion 534 formed as a radial perforation 534. A piston ring 539 opens and closes this conductive channel at its orifice 537 depending on the position of an activation pin. The orientation of the channel portion 534 with respect to the central axis is equivalent to the angle τ of the channel portion 471 of FIG. 301A. The extension wall 535 has an angle equivalent to the angle ω of the wall 476a of FIG. 1A. Also shown is a cylinder wall 538 of the cylinder 536.

Figure 304 shows an actuation pin and its cylinder, which is incorporated into an assembled pipeline housing means 520, 521 etc., in which a valve 522, for example a Schrader valve, with a spring force actuation core pin 523 is arranged. Ru. The actuation pin engages the core pin 523 of the valve.

Figure 305 shows a valve actuator within a universal valve connector. This is equivalent to the one in figure 301, but with the spacing A of the two sealing means 540, 541, two valves of different sizes can be sealed. Two enlargements 1 and 2 of the diameter of cylinder 542 within cylinder wall 550 are shown at intermediate distance B. Also shown is actuation pin 543, with two levels of engagement:
It is indicated by distance B. For example, if the valves are of different types, the intermediate distances may be equal or different, such that the distances from the core pin to the sealing are not the same. Between the two enlarged parts 1 and 2 there is a cylindrical wall part 544 with a cylinder part 545 that fits into the piston ring 508.
There is. Also shown is the central axis 546 from the housing 549, the coupling portion 547, and its opening 548.
19597 Description of preferred embodiments Figure 401A shows a line XX between two of the three engagement surfaces 1, 2 of the base 4 with a rigid surface 5, around which the combination 6 is movable . A line YY between two of the three engaging surfaces 2, 3 of the base 4 and the rigid surface 5, around which the combination 6 can move. base 4 of 3
A line ZZ between two of the two contact points 1, 2 and the rigid surface 5, around which the combination 6 can move.

FIG. 401B shows a combination 6 comprising a chamber 7, a guide 8 for a piston rod 9 and a handle 10. The base 4 with contacts 1, 2 and 3 is rounded towards the rigid surface. Chamber 7 is firmly connected to base 4 by reinforcement 11.

FIG. 402 A shows the handle 10 of the combination 6 when the combination 6 is in its rest position 12 .
FIG. 402B shows the combination 6 in its rest position 12 when the transition 13 between the combination 6 of the base 40 and the rebar 14 is in its rest position. The transition 13 may be made of a flexible material and is arranged around the chamber 7.

FIG. 402C shows the working position 14 of the handle 10 when it has been moved from the rest position 12 in front of said rest position.
FIG. 402D shows the working position 15 of the handle 10 when the handle is moved from the rest position 12 behind said rest position.

Figure 402E shows the operating position 16 of the handle 10 when the handle has been moved from the rest position 12 on the front left side of said rest position.
Figure 402F shows the operating position 17 of the handle 10 when the handle is moved from the rest position 12 on the left rear side of said rest position.

Figure 402G shows the actuated position 18 of the handle 10 when the handle is moved from the rest position 12 on the front right side of said rest position.
Figure 402H shows the actuated position 19 of the handle 10 when the handle is moved from its rest position 12 on the right rear side of said rest position.

Figure 403A shows a floor pump in which the transition between chamber 7 and base 4 is an elastically deformable bushing 20.
Figure 403B shows an enlargement of the transition between chamber 7 and base 40. The chamber 7 has a projection 21 that fits into a groove 22 in the bushing 20, which allows the chamber 7 to be easily installed in the base 40. The protrusion 41 is at the top of the reinforcement 42 of the basis 40.

FIG. 403C shows a floor pump in which the transition between the chamber 7 and the base 4 is an elastically deformable bushing 23 .
FIG. 403 D shows a close-up of the transition between chambers 7 and 40. Chamber 7 has a groove 25 that fits over protrusion 24 of bushing 23, allowing easy attachment of chamber 7 to base 40.

FIG. 404A shows the combination 6 in the form of a floor pump with a cab 25 which allows lateral movement and/or deflection of the piston rod relative to the rest of the combination 6 and base 43. The base 43 is connected to the base 41 either directly by rebar 42 or indirectly, for example by a flexible bushing.

FIG. 404B shows a close-up of the cap 25 of FIG. 404A when the piston 44 is at the end of its stroke furthest from the base 43. The piston rod 9 travels within the guide means 26, the convex contact inner surface 31 of which makes linear contact at the center line 27 of the piston rod 9.
is held within cap 9 by surfaces 36 and 37 and by flexible O-ring 28. The cross-sectional area of space 29 between surfaces 36, 37 of cap 9 and guiding means 26 is shown to be larger than the cross-sectional area of ring 28 itself to allow substantial compression of ring 28 (e.g.
FIG. 404C) Distance a between the outside of the piston rod 9 and the wall 38 of the spaces 33 and 34 of the cab 9. The distance a may be approximately the same as the distance b between the piston rod at the top of the cab and the wall 38 of the cab 9.

Fig. 404C shows Fig. 4B where the central axis 32 of the piston rod 9' is at an angle a offset with respect to the central axis 30 of the rest of the assembly. The space 29' is substantially filled by the compression ring 28', which is compressed by the translation guide means 26'. The space 34'. The space 33'. The contact surface 35 of the guide means 26' with the piston rod 9'. The distance a' is smaller than the distance a in Fig. 404B.

Distance b' is less than distance b in diagram 404B and greater than the difference between distances a and a'.
404D shows an enlargement of the cap 25 of FIG. 404A, where the piston 44 may be at the end of its stroke closest to the base 43. Combination center line 30 cab 25 inner wall 38 and piston rod 9
Spaces between 33 and 34.

FIG. 404E shows FIG. 404D when the piston rod 9' is moved to the left to a distance a" between the outside of the piston rod 9' and the inner wall 38 of the cab 25. When the guiding means 26" is moved to the left, compressing the ring 28", the space 29" is filled in this cross section by the compression ring 28, as shown. The space 33" is approximately equal to the space 34" at an equal distance b" where the distance a" is less than the 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 central axis 54 of the combination 55. The angle a between the central axis 56 of the left part 51 of the handle 52 and the central axis 57 of the right part 53 of the handle 52 is less than 180° as viewed from the user's position X. The center point 61 of the left part 51 and the center point 62 of the right part 53.

FIG. 405B shows a front view of the floor pump of FIG. 5A, including handle 52 and combination 55. The handle 52 is 51 on the left and 53 on the right. Central axis 54 of combination 55.
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 β between the central axis 56 of the left portion 58 of the handle 59 and the central axis 61 of the right portion 60 of the handle 59, when viewed from the user's position X, is greater than or equal to 180°.

FIG. 406B shows a front view of the floor pump of FIG. 406A, including handle 59 and combination 55. The handle 59 has 58 parts on the left (=clockwise 53) and 60 parts on the right (=counterclockwise 51).
507 SUMMARY OF THE INVENTION The valve actuator of the invention and its embodiments are the subject of claims 1 and 2 to 17, respectively. A valve connector and a pressure vessel or manual pump comprising a valve actuator according to the invention are the subject matter of claims 18 and 19, respectively. Claim 20 is directed to the use of the valve actuator in a fixed structure.

The present invention provides a valve actuator with a combination of an inexpensive cylinder with a piston moving to drive the actuation pin and an actuation pin having a simple structure. This combination can be used in fixed structures such as chemical plants where the actuation pin engages a spring-force actuated core pin of a valve (e.g., a release valve), as well as in valve connectors (e.g., for inflating vehicle tires). The shortcomings of conventional valve connectors are overcome by the valve actuator of the present invention. The valve actuator features a piston having a piston ring that fits into the cylinder, and in its first position, the piston is a first predetermined distance from a first end of the cylinder. In its second position, the piston is a second predetermined distance from the first end of the cylinder, the second predetermined distance being greater than the first predetermined distance. The cylinder wall is configured to prevent the piston from moving past the first end of the cylinder.
a conduction channel for allowing conduction of gas and/or liquid medium between the cylinder and the coupling when the piston is in a first position, and conduction of gas and/or liquid medium between the cylinder and the coupling is inhibited by the piston when the piston is in a second position.

An embodiment of the inventive valve actuator as described in claim 6 features a conduction channel from the pressure source to the valve to be actuated, which comprises an enlargement of the cylinder diameter arranged around the piston of the actuation pin at the bottom of the cylinder when the piston is in a first position, allowing the medium to flow from the pressure source, for example from a Schrader valve, to the open spring-pressurized actuation valve core pin. The enlargement of the cylinder diameter may be uniform or the cylinder wall may have a 10 mm diameter enlargement near the bottom of the cylinder, where the distance between the centerline of the cylinder and the cylinder wall increases.
The piston ring may include a plurality of portions, which allows the gas and/or liquid medium to flow freely around the edge of the piston ring when the piston is in the first position. A variation of this embodiment has a valve actuator configuration whose cylinder has an enlargement of twice the diameter. The distance between the enlargements can be the same as the distance between the sealing levels of the sealing means. If three valves of different sizes can be combined, the valve actuator can comprise three enlarged cylinders. However, it is also possible to connect valves of different sizes to a valve actuator having a single configuration for enlarging the diameter of the cylinder. Thus, here the number of enlargements can be different from the number of different sizes of valves that can be combined.

Another embodiment of the invention as defined in claim 10 features a conductive channel through a portion of the body of the valve actuator. The channel forms a passage for gas and/or liquid medium between the cylinder and a portion of the valve actuator connected to the valve. An orifice of the channel opening in the cylinder is arranged such that when the piston is in a first position, pressurized gas and/or liquid medium flowing from the pressure source to the cylinder also flows through the channel to the actuated valve. When the piston is in a second position, the piston blocks the cylinder, preventing the flow of pressurized gas and/or liquid medium to the channel.

Instead of air, any kind of gas and/or liquid (mixture) can actuate the actuating pin and flow around the piston of the valve actuator when the piston is in its first position. The invention can be used for all types of valve connectors that can couple valves with spring-actuated core pins (e.g. Schrader valves), regardless of the coupling method or number of coupling holes of the connector. Furthermore, the valve actuator can be coupled to, for example, a foot pump, a car pump, or a compressor. The valve actuator can also be integrated into any pressure source (e.g. a hand pump or a pressure vessel), regardless of the availability of fastening means in the valve connector. The invention can also be used for permanent constructions where the actuator pin of the actuator engages with the core pin of a permanently attached valve.

The various embodiments described above are provided as examples and should not be construed as limiting the present invention. Those skilled in the art will readily recognize various modifications and changes that can be made to the present invention without strictly adhering to the exemplary embodiments and applications shown and described herein and without departing from the true spirit and scope of the present invention as set forth in the claims.

Claims (151)

1. A piston-chamber combination comprising: a chamber (162, 186, 231) bounded by an internal chamber wall (156, 185, 238); and an actuator piston disposed within the chamber such that the actuator piston is slidable relative to the chamber wall between at least a first longitudinal position and a second longitudinal position of the chamber,
the chamber has a cross-section with different cross-sectional areas and different circumferential lengths at a first longitudinal position and a second longitudinal position, and has at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first longitudinal position and the second longitudinal position, the cross-sectional area and circumferential length at the second longitudinal position being smaller than the cross-sectional area and circumferential length at the first longitudinal position;
the actuator piston comprises a receptacle (208, 208', 217, 217', 228, 228', 258, 258', 450, 450'), the receptacle being elastically deformable to provide different cross-sectional areas and circumferential lengths of the piston and accommodate the different cross-sectional areas and different circumferential lengths of the chamber during relative movement of the piston between a first longitudinal position and a second longitudinal position through the intermediate longitudinal position of the chamber;
the actuator piston is manufactured to have a production size of the vessel (208, 208', 217, 217', 228, 228', 258, 258', 450, 450') in a stress-free and deformation-free state in which a circumferential length of the piston is approximately equal to a circumferential length of the chamber (162, 186, 231) in the second longitudinal direction, the vessel being expandable from its production size transversely to the longitudinal direction, thereby allowing the piston to expand from its production size during relative movement of the actuator piston from the second longitudinal position to the first longitudinal position;
the container (208, 208', 217, 217', 228, 228', 258, 258', 450, 450') is elastically deformable to provide different cross-sectional areas and circumferential lengths of the actuator piston;
- the combination comprises means for introducing fluid into the vessel from a location external to the vessel, thereby enabling pressurization of the vessel, thereby expanding the vessel;
- A piston-chamber combination, characterized in that the wall of the actuator piston presents a smooth surface at least at and close to its area of contact with the wall of the chamber, thereby moving the container from a second position in the chamber to a first longitudinal position. a chamber (162,186,231) bounded by an internal chamber wall (156,185,238); and a chamber within said chamber slidable relative to said chamber wall between at least a first longitudinal position and a second longitudinal position of said chamber. an actuator piston provided in the piston-chamber combination, the piston-chamber combination comprising:
The chamber has a cross-section of different cross-sectional area and different circumferential length at a first longitudinal position and a second longitudinal position, and between the first longitudinal position and the second longitudinal position. have at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions, and the cross-sectional areas and circumferential lengths at said second longitudinal positions are different from said first longitudinal positions. smaller than the cross-sectional area and circumferential length at the directional position,
The actuator piston comprises a container (208, 208', 217, 217', 228, 228', 258, 258', 450, 450'), which can be elastically deformed to accommodate different cross-sectional areas and circumferential lengths of the piston. providing that during relative movement of the piston between a first longitudinal position and a second longitudinal position through the intermediate longitudinal position of the chamber, the different cross-sectional areas and different circumferential directions of the chamber; adapting the piston to a length;
The actuator piston is arranged in a stress-free and undeformed state in which the circumferential length of the piston is approximately equal to the circumferential length of the chamber (162, 186, 231) in the second longitudinal direction. , 258,258', 450,450'), said container being expandable from said production size in a direction transverse to said longitudinal direction, whereby from said second longitudinal position during relative movement of the actuator piston to the first longitudinal position, the piston can be expanded from its production size;
the container (208, 208', 217, 217', 228, 228', 258, 258', 450, 450') is elastically deformable and comprises a closed space to provide different cross-sectional areas and circumferential lengths of the actuator piston;
- the combination provides means for varying the volume of the enclosed space communicating with the actuator piston of the container from a position outside the container, thereby enabling pressurization of the container, thereby inflating the container; Prepare,
- the wall surface of the actuator piston provides a smooth surface at least in its contact area with the wall of the chamber and close to the contact area, such that the container can be moved from the second position of the chamber to the first position; A piston-chamber combination characterized by movement into longitudinal position. 3. A piston-chamber combination as claimed in claim 1 or 2, wherein the actuator piston inside or outside the chamber is sealably moveable relative to the chamber wall. 4. A piston-chamber combination according to claim 1, 2 or 3, wherein parts of the chambers located adjacent to the actuator piston communicate with each other via channels or via the atmosphere. 15. A piston-chamber combination according to any one of claims 14, wherein the chamber is elongated. A piston-chamber combination according to any one of claims 1 to 4, wherein the chamber is circular. 7. The piston-chamber combination of claim 6, wherein the chamber is formed about a circular central axis. A piston-chamber combination according to any one of claims 1 to 7, wherein the actuator piston is under pressure and does not engage the walls of the chamber. 9. The piston-chamber combination of claim 8, wherein the piston is moving from a first longitudinal position to a second longitudinal position of the chamber. A piston-chamber combination according to any one of claims 1 to 7, wherein a portion of the length of the wall of the chamber is parallel to the central axis of the chamber. 11. The piston-chamber combination of claim 10, wherein the wall of the chamber is located at the end of the stroke of the actuator piston. 8. The piston-chamber combination of any one of claims 1 to 7, wherein the container (208, 208', 217, 217', 228, 228', 258, 258', 450, 450') comprises a deformable material (205, 206). Piston-chamber combination according to claim 12, wherein the deformable material (205, 206) is a fluid or a mixture of fluids, such as water, steam and/or gas, or a foam. In a cross-section through the longitudinal direction, the container is arranged in the first longitudinal position of the chamber (186, 231), and when the container is arranged in the second longitudinal position of the chamber, 14. A piston-chamber combination according to claim 12 or 13, having a first shape different from the second shape. The piston-chamber combination of claim 14, wherein at least a portion of the deformable material (206) is compressible and the first shape has an area that is greater than an area of the second shape. 15. The piston-chamber combination of claim 14, wherein the deformable material (206) is at least substantially incompressible. A piston-chamber combination according to any one of claims 1 to 7, wherein the container is expandable. 8. The piston-chamber combination of claim 1, wherein the container (208, 208', 217, 217', 228, 228', 258, 258', 450, 450') further comprises an enclosed space (210, 243) in communication with the deformable container. The piston-chamber combination of claim 18, wherein the introduction of the fluid into the container from a location outside the container is via a first closed space that communicates with the closed space. The piston-chamber combination of claim 1, 3 or 7, further comprising means for removing fluid from the reservoir to a location outside the piston, thereby allowing the reservoir to contract. 21. The piston-chamber combination of claim 20, wherein the removal of fluid is via a second closed space communicating with the closed space. The means communicates with the enclosed space of the piston by changing the volume of the enclosed space, increasing the volume and thereby depressurizing the actuator piston, thereby allowing deflation of the container. Piston-chamber combination according to any one of claims 2 to 7 or 18, characterized in that: The piston-chamber combination of claim 22, wherein the piston is movable relative to the chamber wall from at least a first to a second longitudinal position of the chamber. Piston-chamber combination according to any of the preceding claims, wherein the walls of the container (208,208', 217,217', 228,228', 258,258', 450,450') are provided with a bendable reinforcing layer. A piston-chamber combination according to any one of the preceding claims, characterized in that the cross-section of the contact surface of the container and the wall of the chamber cuts the central axis of the cross-section of the container in a longitudinal direction approximately transverse to the approximate centre of the cross-section of the wall of the elastically deformable container, on the side of a second longitudinal position. The cross-section of the contact surface of the container and the wall of the chamber is such that the central axis of the cross-section of the container is at the side of a second longitudinal position and the central point of the cross-section of the container. 26. The piston-chamber combination of claim 25, wherein the piston-chamber combination is cut longitudinally approximately outside of the piston-chamber combination. The piston-chamber combination of claim 12, 17, 20 or 22, wherein the actuator piston comprises a piston rod comprising the enclosed space. 27. A piston-chamber combination according to claim 26, wherein the piston rod comprises engagement means on the outside of the chamber. The piston-chamber combination of claim 28, further comprising a crank configured to translate motion of the piston between a second longitudinal position of the chamber and a first longitudinal position into rotation of the crank. 29. The piston-chamber combination of claim 28, wherein the crank converts rotation thereof into movement of the piston from a first longitudinal position to a second longitudinal position of the piston. The piston-chamber combination of claim 19, 21 or 28, wherein the crank comprises the first and second sealed spaces. 8. The cross-sectional area of the chamber at its second longitudinal position is between 95 and 15% of the cross-sectional area of the chamber at its first longitudinal position. A combination of. 8. The cross-sectional area of the chamber at the second longitudinal position of the chamber is approximately 50% of the cross-sectional area of the chamber at the first longitudinal position of the chamber. Combinations listed. The combination of any one of claims 1 to 7, wherein the cross-sectional area of the chamber at the second longitudinal position of the chamber is about 5% of the cross-sectional area of the chamber at the first longitudinal position of the chamber. 7. The combination according to claim 1, wherein the chamber comprises a convex wall of a longitudinal section near a first longitudinal position, the chambers being divided upwardly from one another by a common boundary, the distance between two common boundaries defining a height of the longitudinal section walls, the height decreasing with increasing overpressure ratio of the actuator piston relative to the pressure in the chamber, and the cross-sectional length of the common boundary being determined by a maximum work force of the actuator piston constant relative to the common boundary. 7. The combination of claim 1, wherein the chambers include convex walls of a longitudinal cross section proximate a first longitudinal position, the chambers being divided upwardly from one another by a common boundary, a distance between two common boundaries defining a height of the longitudinal cross-sectional walls, the height decreasing in a direction from a first longitudinal post to a second longitudinal position, and a cross-sectional length of the common boundary being determined by a maximum work force of the actuator piston, the cross-sectional length being constant relative to the common boundary. 37. A combination according to claim 35 or 36, wherein the chamber further comprises a wall parallel to the central axis of the chamber. The combination of claims 35-37, wherein the chamber further comprises a concave wall. The combination of claim 38, wherein the chamber further includes a transition between the convex wall and the parallel wall, and the transition may include a concave wall. A shock absorber,
- the combination according to any one of claims 1 to 39;
- means for engaging a piston from a position external to said chamber, said engaging means comprising an external position in which said piston is in a first longitudinal position of said chamber and a position in which said piston is in said second longitudinal position; means having an inner position in a longitudinal position of the
Equipped with a shock absorber. 41. The shock absorber according to claim 40, further comprising a closed space communicating with the container. 42. The shock absorber according to claim 41, wherein the closed space has a variable volume. 42. The shock absorber according to claim 41, wherein the closed space has a constant volume. 42. The shock absorber of claim 41, wherein the enclosed space is adjustable. The container and the enclosed space form an at least substantially sealed cavity containing a fluid, the fluid being compressed by the piston moving from the first longitudinal position to the second longitudinal position of the chamber. Shock absorber according to any one of claims 41 to 44, wherein the shock absorber is compressed when A pump for pumping fluid,
A combination according to any one of claims 1 to 39;
means for engaging a second piston in a second chamber from a location outside the chamber;
a fluid inlet connected to said second chamber and comprising valve means; and a fluid outlet connected to said second chamber;
Equipped with a pump. A pump for pumping fluid,
A combination according to any one of claims 1 to 39;
means for engaging a piston within the chamber from a location external to the chamber;
a fluid inlet connected to said chamber and comprising valve means;
a fluid outlet connected to the chamber;
Equipped with a pump. 47. or claim 46, wherein the engagement 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 of the chamber. Pump described in 47. 47. or claim 46, wherein the engagement means has an outer position in which the piston is in the second longitudinal position of the chamber and an inner position in which the piston is in the first longitudinal position of the chamber. Pump described in 47. Use of a piston-chamber combination according to claim 1 or 2 in a motor, in particular an automobile motor. A motor equipped with the piston-chamber combination described in claim 1. A motor, characterized in that it is fitted with a piston-chamber combination according to claim 2. 52. The motor according to claim 1, 3, 39, 46, or 51, wherein the crankshaft includes a second enclosed space that communicates with an external pressure source at one end and communicates with the enclosed space of the actuator piston at the other end. The crankshaft has a third piston that communicates with the sealed space of the actuator piston.
54. The motor according to claim 53, comprising an enclosed space at one end thereof in communication with a compressor pump in communication with an electric motor, said motor obtaining energy from a battery charged by an energy source such as solar power, or a fuel cell 6r such as a H2 fuel cell, or an alternator in communication with said main shaft. The motor of claim 54, wherein the alternator is in communication with the shaft of an auxiliary power source, such as a combustion motor that burns H2 derived from electrolysis of conductive water and O2 of the air coning water from a tank that can be filled externally. The aforementioned pump is in communication with the shaft of an auxiliary power source, such as a combustion motor that burns H2 derived from the electrolysis of conductive water, the water being obtained from a tank that can be filled externally. 55. The motor of claim 54, wherein the motor is air O2. 54. The motor of claim 53, wherein the communication between the pressure source and the enclosed space of the actuator piston occurs during a portion of each crankshaft rotation. The motor of claim 54, wherein the communication between the sealed space of the piston and the recompression cascade occurs during a portion of each crankshaft revolution. 59. A motor according to claim 57 or 58, wherein the communications are temporally separated from each other. 60. The motor of claim 59, wherein the communication is provided by a T-valve and controlled by a computer in electrical communication with a main shaft of the motor. The motor of claim 60, wherein the pressure and/or volume of the supply channel to the T-valve is controlled by a speed reducer valve, which in turn is controlled by a speed increaser. While the at least one pump is in communication with the electric motor, the at least one pump is [
the crankshaft is in communication with a pressure storage vessel which is in communication with a repressurization cascade of a pump which is in communication with the main shaft; the motor is connected to an energy source such as a solar cell; 62. The motor of claim 61, wherein the motor obtains energy from a battery charged by an alternator, or a fuel cell, such as an H2 fuel cell, or an alternator in communication with the main shaft. The motor of claim 62, wherein the alternator is in communication with the shaft of an auxiliary power source, such as a combustion motor combusting H2 by electrolysis of conductive water, and the O2 of the air comes from a tank that can be filled externally. The motor of claim 63, wherein the pump is in communication with the shaft of an auxiliary power source, such as a combustion motor that burns H2 by electrolysis of conductive water, the water being O2 of air supplied from a tank that can be filled externally. A motor according to any one of claims 62 to 64, wherein the pump is a piston pump or a rotary pump. The motor according to any one of claims 2 to 39, 46 to 51, wherein the closed space, the second closed space and the third closed space form a closed cavity. 66. The pressure within the cavity is controlled by a piston-chamber combination in communication with a bidirectional piston-chamber, the combination being controlled by a speed reduction valve, and the speed reduction valve being controlled by a speeder. Motors listed in The bidirectional actuator piston-chamber combination is in communication with a pressure vessel, and the vessel is in communication with a compression ratio cascade of pumps, and at least one of the pumps (of the crankshaft, the other at least one pump is in communication with the main shaft (via a crankshaft of the pump), while the at least one pump is in communication with an electric motor, the motor comprising:
68. A motor according to claim 67, which derives its energy from an energy source such as solar power and/or electricity from a fuel cell such as an H2 fuel cell and/or from an alternator in communication with the main shaft. The motor of claim 68, in which the pump is in direct communication with the shaft of a combustion motor that burns H2 obtained from electrolysis of conductive water, and an auxiliary power source such as O2 from air, the water being obtained from a refillable tank and, if necessary, from a conductive means storage tank. A motor as claimed in any one of claims 67 to 69, wherein the pressure in the cavity is additionally controlled by a piston-chamber combination in communication with the pressure vessel. 66. The motor of claim 65, wherein the pressure within the closed cavity of the piston is controlled by a piston-chamber combination, which combination is in electronic communication with the main shaft of the motor by a computer. the pressure in the closed cavity of the piston is controlled by a piston-chamber combination that communicates with the main shaft of the motor via a cam wheel that communicates with a camshaft;
66. A motor according to claim 65. The motor of claim 61 or 70, wherein the pump is a piston pump or a rotary pump. A motor as claimed in any one of claims 1 to 4, 6 to 73, wherein the piston rotates about the central axis of the chamber. 74. A motor according to any one of claims 1-4, 6-73, wherein the chamber is rotating. 76. A motor according to claim 74 or 75, wherein the piston and the chamber are rotating. 77. A motor according to any one of claims 74 to 76, wherein the actuator piston-chamber combination comprises at least two sub-chambers with actuator pistons, the sub-chambers being arranged successively to one another such that a first circular location of a sub-chamber is adjacent to a second circular location of another adjacent sub-chamber. The motor of claim 77, wherein the subchambers are identical. The motor of claim 78, characterized in that each sub-chamber comprises an actuator piston, the pistons being identical and each piston being disposed at a different circular position relative to each other in each sub-chamber. A motor according to any one of claims 74 to 79, wherein the shape of the piston does not change during the stroke. 69. A motor according to claim 62 or 68, wherein the pressure vessel is pressurized by an external pressure source via a pluggable connection. The motor of claim 54, 62 or 68, wherein the battery is charged by an external power source via a plug connection. an elongated chamber (70) bounded by internal chamber walls (71, 73, 75) and a piston means (76, 76', 163) within said chamber, said piston means being arranged to move at least a first portion of said chamber;
and a second longitudinal position, the piston-chamber combination being sealably movable relative to the chamber between said first longitudinal position and said second longitudinal position,
the chamber has a cross-sectional area that differs between a first longitudinal position and a second longitudinal position of the chamber, the cross-sectional area being at least substantially continuously different at an intermediate longitudinal position between the first longitudinal position and the second longitudinal position of the chamber, the cross-sectional area at the first longitudinal position being greater than the cross-sectional area at the second longitudinal position;
said piston means being designed to adapt itself and the sealing means to said different cross-sectional areas of said chamber during relative movement of said piston means from a first longitudinal position of said chamber through said intermediate longitudinal position to a second longitudinal position;
said piston means (76, 76', 163, 189, 189') comprising a plurality of at least substantially rigid support members (81, 82, 184) rotatably secured to a common member (6, 23, 45, 180);
said support member is provided with elastically deformable means (79) carried by said support member for sealing against an inner wall (71, 73, 75, 155, 156, 157, 158) of said chamber (70), said support member being rotatable between 10° and 40° relative to a longitudinal axis (19) of said chamber (70);
A piston-chamber combination, characterized in that the support member (81, 82, 184) is bendable. 84. The piston-chamber combination of claim 83, wherein the piston is inside or outside the piston so as to be sealingly movable with respect to the chamber wall. 84. The piston-chamber combination of claim 83, wherein the support member has a predetermined bending force. 84. A piston-chamber combination as claimed in claim 83, wherein said support member (81, 82, 184) is rotatable at least approximately parallel to said longitudinal axis (19). The piston-chamber combination of claim 83, wherein the elastically deformable means (79) is made of polyurethane foam. The piston combination of claim 87, wherein the polyurethane foam comprises polyurethane memory foam and polyurethane foam. 89. The piston-chamber combination of claim 88, wherein the polyurethane foam is a major portion of polyurethane memory foam and a minor portion of polyurethane foam. The piston-chamber combination of any one of claims 87 to 89, wherein the polyurethane foam is provided with a flexible water-blocking layer. 91. The piston-chamber combination of claim 90, wherein the impermeable layer has a non-stress producing size the periphery of which is approximately equal to the circumference of the wall of the chamber at a second longitudinal or circular position. 87. A piston-chamber combination according to claim 83 or 86, wherein the common member is attached to a crankshaft. 90. A piston-chamber combination as claimed in claim 83 or 88, wherein the common member is attached to the piston-chamber combination which is an external bi-directional actuator. an elongated chamber (70) bounded by internal chamber walls (71, 73, 75) and a piston means (76, 76', 163) within said chamber, said piston means being arranged to move at least a first portion of said chamber;
and a second longitudinal position, the piston-chamber combination being sealably movable relative to the chamber between said first longitudinal position and said second longitudinal position,
the chamber has a cross-sectional area that differs between a first longitudinal position and a second longitudinal position of the chamber, the cross-sectional area being at least substantially continuously different at an intermediate longitudinal position between the first longitudinal position and the second longitudinal position of the chamber, the cross-sectional area at the first longitudinal position being greater than the cross-sectional area at the second longitudinal position;
said piston means being designed to adapt itself and the sealing means to said different cross-sectional areas of said chamber during relative movement of said piston means from a first longitudinal position of said chamber through said intermediate longitudinal position to a second longitudinal position;
The piston means (49, 49') comprises a plurality of at least substantially rigid support members (43) rotatably secured to a piston rod (45) by an axle (44);
the support member is supported by a sealing means (41) supported by a spring 42 for sealing against an inner wall (71, 73, 75, 155, 156, 157, 157, 158) of the chamber (70), the support member being rotatable between 1° and 2° with respect to a longitudinal axis (19) of the chamber (70);
A flexible water-impermeable film (sheet) (40) is attached to the sealing means (O-ring) (41),
A central axis (19) of the chamber (1) is arranged perpendicular to the central axis (19),
The membrane (flexible impermeable sheet) includes a reinforcing layer;
The support member (means), the sealing means (O-ring), the flexible impermeable membrane (sheet) and the spring (lay) are vulcanized together;
A piston-chamber combination characterized in that The piston-chamber combination of claim 94, wherein the support member (81-, 82, 184) (means) is rotatable at least approximately parallel to the longitudinal axis (19). 95. The piston-chamber combination of claim 94, wherein the flexible reinforcement layer (sheet) comprises a helical reinforcement. 95. A piston-chamber combination according to claim 94, wherein the reinforcing layer (sheet) comprises concentric reinforcements arranged around the central axis of the chamber. The piston-chamber combination of claim 94, wherein the flexible impermeable membrane (sheet) has an angle of greater than 90° with respect to the central axis of the chamber. 99. The piston-chamber combination of claim 98, wherein the flexible water-blocking membrane (sheet) is mounted on the piston rod. The piston-chamber combination of claim 98, wherein the flexible impermeable membrane (sheet) is vulcanized onto the piston rod. 95. A piston-chamber combination according to claim 83 or 94, wherein the common member comprises a piston-chamber combination. 95. The piston-chamber combination of claim 94, wherein the flexible impermeable sheet is supported by foam. The piston-chamber combination of claim 102, wherein the foam is reinforced with a rigid member rotatably fixed to the piston rod. 1. The piston-chamber combination comprising a chamber (162, 186, 231) bounded by an internal chamber wall (156, 185, 238) and piston means within the chamber, the piston means being slidable relative to the chamber between at least a first longitudinal position and a second longitudinal position of the chamber,
the chamber has a cross-section with different cross-sectional areas and different circumferential lengths at a first longitudinal position and a second longitudinal position, and has at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first longitudinal position and the second longitudinal position, the cross-sectional area and circumferential length at the second longitudinal position being smaller than the cross-sectional area and circumferential length at the first longitudinal position;
The piston means is a resiliently deformable container (208, 208', 217, 217', 228, 228', 258, 258'
, 450, 450') to accommodate different cross-sectional areas and circumferential lengths of said piston means to different cross-sectional areas and circumferential lengths of said chamber during relative movement of said piston through said intermediate longitudinal position of said chamber and between said first longitudinal position and said second longitudinal position;
said piston means being manufactured to have a production size of the vessel (208, 208', 217, 217', 228, 228', 258, 258', 450, 450') in a stress-free and deformation-free state in which a circumferential length of said piston means is approximately equal to a circumferential length of said chamber (162, 186, 231) in said second longitudinal direction, said vessel being expandable from its production size transversely to said second longitudinal direction, thereby providing an expansion of said piston means from its production size during relative movement of said actuator piston from said second longitudinal position to said first longitudinal position;
said container (208, 208', 217, 217', 228, 228', 258, 258', 450, 450') being elastically deformable to provide different cross-sectional areas and circumferential lengths of said piston means;
said piston means (92, 92', 146, 146', 168, 168', 208, 208', 222, 222', 222") comprises an elastically deformable container containing a deformable material (103, 103', 124, 124', 136, 137, 173, 173', 174, 174', 205, 205', 206, 206', 215, 215', 219, 219');
A piston-chamber combination characterized in that The piston-chamber combination of claim 104, wherein the container within the chamber is sealably movable relative to the chamber wall. The deformable material (103, 103', 124, 124', 136, 137, 173, 173', 174, 174', 205, 20
Piston according to claim 104 or 105, wherein 5', 206, 206', 215, 215', 219, 219') is a fluid or a mixture of fluids, such as water, steam and/or gas, or a foam. -Chamber combination. The piston-chamber combination of claim 106, wherein the deformable material (124, 124', 136, 174, 174', 205, 205', 219, 219') is at least substantially incompressible. 108. A piston-chamber combination as described in claim 106 or 107, wherein the container is expandable. The piston-chamber combination of claim 104 or 105, further comprising a piston rod, the walls of the container comprising a flexible material, the flexible material being vulcanized onto the piston rod. The piston-chamber combination of claim 109, wherein the wall of the container is positioned proximate to the piston rod and comprises at least one layer having a vulcanized reinforcement thereon and one layer above said layer that does not include a vulcanized reinforcement. 111. The piston-chamber combination of claim 110, wherein the reinforcement member stress is arranged parallel to the central axis of the piston and is bendable. 110. A piston-chamber combination as claimed in claim 108 or 109, wherein the wall of the container comprises two reinforcing layers, the reinforcing materials of said layers intersecting each other at a very small angle. The length of the container-type piston is expanded such that the shape of the elliptical piston in the second longitudinal position is maintained if it is in the first longitudinal position, but not its size. , a piston-chamber combination according to any of the claims. 52. The motor of claim 51, wherein the pressure regulator in communication with the pressure vessel and the third enclosed space is in communication with the speeder. The motor according to claim 51, further comprising two cylinders, the third sealed spaces of the cylinders communicate with each other through a connection between the two sub-crankshafts included in the crankshaft of the motor, and the second sealed spaces of the cylinders communicate with each other outside the crankshaft (FIG. 19). 116. The motor of claim 115, wherein the crankshaft arrangements of the two piston-chamber combinations are positioned 180 degrees from each other. (FIG. 19) The motor according to claims 115 and 116, further comprising two or more cylinders, wherein a second sealed space is connected through the connection of the sub-crankshafts of two existing cylinders, and the second sealed space of the sub-crankshaft of the cylinder is added. (FIG. 19) 53. The motor of claim 52, further comprising two cylinders, the second longitudinal position of one cylinder being at the same geometric level as the first longitudinal position of the second cylinder, both actuator pistons communicating with each other via a crankshaft, the crankshaft comprising two connected sub-crankshafts, one sub-crankshaft for each actuator piston, the connecting rods to the actuator pistons being positioned 180 degrees from each other. (FIG. 17) further comprising an ESVT pump for each of said cylinders;
With respect to the two cylinders, the pump is configured to:
119. The motor of claim 118, wherein the motor is combined with one pump, the enclosed space is contained within the crankshaft, and the enclosed spaces communicate with each other at a connection point of the sub-crankshafts. (Figure 17) Further comprising a valve for opening and closing the connection between the ESVT pump and the second or third sealed space, each connection having a check valve or non-return valve function, and the valve 120. Motor according to claim 119, controlled by pressure and/or tappet, said tappet communicating with a camshaft communicating with the main shaft of the auxiliary motor. (Figure 17) The motor according to any one of claims 118 to 120, further comprising two or more cylinders, each additional cylinder communicating with the existing sub-crankshaft through a sealed space of the connected sub-crankshaft. (FIG. 17) 53. The motor of claim 52, further comprising two cylinders, the first longitudinal position of one cylinder being at the same geometric level as the first longitudinal position of the second cylinder, both actuator pistons communicating with each other via a crankshaft, the crankshaft comprising two connected sub-crankshafts, one sub-crankshaft for each actuator piston, the connecting rods to the actuator pistons being positioned at 0° with respect to each other (FIG. 18). further compressing the ESVT pump for each of the cylinders, the pump communicating the enclosed space of one of the actuator pistons with the enclosed space of another of the actuator pistons; By means of said 2
123. The motor of claim 122, which is combined into one pump for two cylinders, the enclosed spaces being contained within the crankshaft, and the enclosed spaces communicating with each other at connection points of the sub-crankshafts. (Figure 18) Further comprising a valve for opening and closing the connection between the ESVT pump and the second or third sealed space, each connection having a check valve or non-return valve function, and the valve 124. Motor according to claim 123, controlled by pressure and/or tappet, said tappet communicating with a camshaft communicating with the main shaft of the auxiliary motor. (Figure 18) further comprising two or more cylinders, the enclosed space of each additional (combined) cylinder is separated through a filler connected to said existing sub-crankshaft, and the power stroke of the added cylinder is simultaneously 125. A motor according to any one of claims 122 to 124, wherein the motor is a cylinder return stroke. (Figure 18) The motor of claim 52, further comprising two cylinders, the connecting rods being at 180° to each other and the chambers having the same geometrical position of their first and second longitudinal positions. (FIG. 18) The piston-chamber combinations for each of the enclosed spaces in the sub-crankshaft varying the speed/pressure in the cylinders communicate with each other via the electric pressure regulator of the two-way actuator, 127. A motor according to any one of claims 115 to 126, in communication with the external speeder. A motor as claimed in any one of claims 115 to 127, wherein the piston rod of the pump which pressurises fluid in the piston is powered by a two-way actuator piston powered by a battery powered by an auxiliary power source. A motor as claimed in any one of claims 115 to 128, wherein the piston rod of the pump which pressurises fluid in the piston is powered by a two-way actuator piston powered by a battery powered by an auxiliary power source. A motor as claimed in any one of claims 115 to 129, wherein the piston rod of the pump which pressurises fluid in the piston is powered by a two-way actuator piston powered by a crankshaft powered by an auxiliary power source. A motor as claimed in any one of claims 115 to 130, wherein the piston rod of the pump which pressurises fluid in the piston is powered by a two-way actuator piston powered by a clam shaft powered by an auxiliary power source. 53. The motor of claim 52, comprising a circular chamber and an actuator piston, the piston rod being sealably movable within a cylinder, the sealed space within the piston rod communicating with a pressure controller communicating with a remotely positioned speeder, while the size of the sealed space is adjusted by a pump having a conical chamber whose end runs on a cam profile, the cam profile rotating the cam, the motor being driven by an auxiliary electric motor rotating independently about the same main motor shaft. 5. The actuator piston has a wall and a reinforcement, the wall being attached to a fixed end on the piston rod and a movable end capable of sealing on the piston rod. The motor described in 132. It comprises an elongated chamber (70) bounded by an internal chamber wall (71, 73, 75) and piston means (76, 76', 163) within said chamber, said piston means said at least a first
said piston-chamber combination sealingly movable relative to said chamber between a longitudinal position and a second longitudinal position;
The chamber has a cross-section with a different cross-sectional area at a first longitudinal position and a second longitudinal position of the chamber, and between the first longitudinal position and the second longitudinal position of the chamber. have at least substantially continuously different cross-sectional areas at intermediate longitudinal positions, the cross-sectional area at the first longitudinal position being greater than the cross-sectional area at the second longitudinal position;
Said piston means is configured to move said different sections of said chamber during relative movement of said piston means from a first longitudinal position of said chamber through said intermediate longitudinal position to a second longitudinal position. designed to accommodate the piston means itself and the sealing means in an area;
The piston means (1300) includes a plurality of reinforcing pins (1302, 1303, 1304) rotatably fixed to a holder plate (1307) constituted by a holder (1308),
Said reinforcing pin is provided within a resiliently flexible foam supported by said reinforcing pin, said reinforcing pin being arranged in said chamber (70) for sealing an inner wall (XXXX) of said chamber (70). further comprising an impermeable layer 1305 that is rotatable between 0° and 40° with respect to the longitudinal axis (1319) of ) and is elastically flexible;
The reinforcing pin is made of metal;
The holder plate is made of metal and has small closed rounded end holes (1329, 1330,
1331) in more than one row (1326, 1327, 1328), the reinforcing pins are fixed to the holder plate by magnetic force,
A piston-chamber combination characterized by: 1. The piston-chamber combination comprising an elongated chamber bounded by an internal chamber wall, and a piston means (76, 76', 163) within the chamber, the piston means being sealably movable relative to the chamber between at least a first longitudinal position and a second longitudinal position of the chamber,
the chamber has a cross-sectional area that differs between a first longitudinal position and a second longitudinal position of the chamber, the cross-sectional area being at least substantially continuously different at an intermediate longitudinal position between the first longitudinal position and the second longitudinal position of the chamber, the cross-sectional area at the first longitudinal position being greater than the cross-sectional area at the second longitudinal position;
said piston means being designed to adapt itself and the sealing means to said different cross-sectional areas of said chamber during relative movement of said piston means from a first longitudinal position of said chamber through said intermediate longitudinal position to a second longitudinal position;
said piston means comprising an elastically deformable container containing a deformable material, the deformable material being a fluid or mixture of fluids such as water, steam and/or gas, or a foam;
the vessel wall includes separate wall portions (2106, 2112, 2113, 2123, 2133, 2142, 2143, 2207, 22xx, 22xx, 2244, 2244"), the separate wall portions having a greater perimeter than the remainder of the vessel wall and including an area in contact with the chamber wall;
A piston-chamber combination characterized in that It comprises an elongated chamber (70) bounded by an internal chamber wall (71, 73, 75) and piston means (76, 76', 163) within said chamber, said piston means said at least a first
said piston-chamber combination sealingly movable relative to said chamber between a longitudinal position and a second longitudinal position;
The chamber has a cross-section with a different cross-sectional area at a first longitudinal position and a second longitudinal position of the chamber, and between the first longitudinal position and the second longitudinal position of the chamber. have at least substantially continuously different cross-sectional areas at intermediate longitudinal positions, the cross-sectional area at the first longitudinal position being greater than the cross-sectional area at the second longitudinal position;
Said piston means is configured to move said different sections of said chamber during relative movement of said piston means from a first longitudinal position of said chamber through said intermediate longitudinal position to a second longitudinal position. designed to accommodate the piston means itself and the sealing means in an area;
The piston means (1300) includes a plurality of reinforcing pins (1352, 1353, 1354) rotatably fixed to a holder plate (1358) constituted by a holder (1359),

Said reinforcing pin is provided within a resiliently flexible foam supported by said reinforcing pin, said reinforcing pin being arranged in said chamber (70) for sealing an inner wall (XXXX) of said chamber (70). further comprising an impermeable layer (1305) rotatable between 0° and 40° with respect to the longitudinal axis (1319) of ) and elastically flexible;
The reinforcing pin is made of plastic with a spherical end (1355, 1356, 1357),
the holder plate includes more than one row (1326, 1327, 1328) of small closed, rounded spherical cavities (1360, 1361, 1362);
the spherical end fits into the rounded spherical cavity;
The holder plate further includes openings (1363, 1364, 1365) for guiding the reinforcing pins.
A piston-chamber combination characterized by: The piston (4000) is disposed at a center point (399) of the chamber.
5) having a connecting rod (4003) having a central axis (4008), and a shaft (4002) having a central axis, the piston (4000) being connected to the shaft (4002) by the connecting rod (4003). The motor of claim 137, wherein the connecting rod (4003) is disposed perpendicular to the shaft (4002), and the central axis (4008) of the connecting rod (4003) and the central axis of the shaft (4002) pass through the center point (3995). The connecting rod (4003) is connected to the piston (4000) via an extension rod (4020), and is connected to the intersection (3990) of the central axis (4008) of the connecting rod (4003) and the center of the chamber (4001). Motor according to claim 137 or 138, further comprising an extension rod (4020), the distance (1,1') between the axis (3996) and the end (3991) of the extension rod (4020) being variable. . The piston (4000) further comprises a pressure management system and a hub for mounting the connecting rod on the axle, the piston (4000) being connected to a channel (4004) of the axle (4002), a channel (4006) in the wall of the axle (4002), a channel (4006') in the hub (4009), a channel (4005) of the connecting rod (4003), and a channel (4025) in the extension (4020) of the piston (4000) into a space (4026).
139. The motor of claim 137 or 138, wherein the motor is in communication with the pressure management system through a channel (4027) in the extension rod (4020). The motor according to any one of claims 137 to 140, wherein the hub (4009) includes a counterweight (3994). 5. The axle (4002) is slidably attached to the connecting rod (4003) by a hub (4009) comprising teeth (4007) that fit into grooves (4007') of the axle (4002). The motor described in any one of paragraphs 137 to 141. Channels (4025), (4005), (4006'), (4006) and (4008) of the extension rod (4020), the connecting rod (4003), the wall of the hub (4009), the axle (4002) 143. The motor of claim 142, wherein communication between an interior (4026) of the piston (4000) and the pressure management system, through a wall and the axle (4002), respectively, is constant. the axle (4032) is connected to the connecting rod (4033) by a hub (4038) having teeth (4007) which fit into grooves (4007') of the axle (4002);
Further, the annular chamber (4001) is connected via spokes (4034) attached to a hub (4035), and a bearing (4039) is disposed between the hub (4035) and the axle (4002);
The motor according to any one of claims 137 to 143, comprising a channel (4043) between the hub (4038) connected to the connecting rod (4033) and the axle (4032) that is in constant communication with the channel (4046) of the connecting rod (4033) through the channel (4045) in the wall of the hub (4038) and the channel (4034) of the axle (4032) through the channel (4044) in the wall of the axle (4032) (Figure 91B). The bearing (5100) is a part of the hub (5101) that assembles the shaft (5102) to the axle (5103), and connects the spoke (5105) (suspending the chamber) to the axle (5103). the connecting rod (5102) has a channel (5109), the axle (5103) has a channel (5114), and the communication between the channels A motor according to any one of claims 137 to 144, wherein is interrupted by the bearing (5100). (Figure 91C,D) The motor of claim 44 or 145, wherein the axle (4002) comprises an additional channel (4041) that is a reduced diameter portion (4046) of the axle (4040) and is located near the channel (4042) in the wall of the portion (4046). 47. The motor of claim 46, wherein communication between a channel (4035) of the connecting rod (4003) and a channel (4034) of the axle (4032) is constant. further comprising three circular chambers in which the piston moves, a housing, a hub, a motor shaft, and a gearbox, the chambers (4092) being positioned parallel to each other and mutually interconnected by the housing (4095). connected, said piston ((4091) is assembled on said motor shaft (4094) by a hub (5005), said motor shaft (4094) is connected to said gearbox (4093) comprising a drive shaft shaft (5000). In direct communication with said shaft (5004), a channel (5002) in said motor shaft (4094) communicates with an enclosed space (5003) of each piston (4091) and in communication with a pressure management system (5001). , the motor according to any one of claims 137 to 147. Three circular chambers in which the pistons move, a housing plate, a motor shaft,
and a gear having a variable pitching wheel and a variable belt, the chambers being connected to each other by the housing plate (5017), the piston (5011) being connected to the motor shaft (5013) by a connecting rod (50xx) and a hub (5019), pitching wheels (5014) being arranged on each side of the motor (5010), the variable pitching wheels (5014) being connected to corresponding wheels (5015) by belts (5021) attached to wheel axles 5016 of a vehicle, the variable pitching wheels (5014, 5015; 5014', 5015') may be pitched low and high, and the distance x between the wheel axles 5016 of the pitching wheels (5014, 5015; 5014', 5015') does not change. It further comprises three rotating circular chambers, a central axis, a hub, corners on each side of the chambers, an external gearbox, and a pressure management system.
the corners (5023, 5023') are connected to each chamber (5021), the central shaft (5022) comprises a bearing (5033) and an inner shaft (5032), the inner shaft (5032) comprises a channel (5037) communicating with the inner space (5038) of each piston (5025) via a channel (5039) of the connecting rod, the central shaft (5022) comprises an outer portion (5022') of each hub (5022') of each piston (5034),
A motor according to any one of claims 137 to 147, further comprising a bearing (5033) including a portion (5033') corresponding to said portion of the central shaft (5022), the hub (5034) being attached to the inner shaft (5032), the central shaft (5022) communicating with an external gearbox (5024), and each chamber (5021) comprising a ring (5026) located furthest from the central shaft (5022). a pressure management system and a vehicle on each wheel, in particular on two parallel arranged wheels,
A motor as described in any one of claims 1 to 150, wherein the wheels can pivot about a center and the pressure management system (1983) for each of the motors (1970, 1971) is controlled by rotation angles a and b, where angle a > b, via control signals (1984, 1985) transferred to each of the motors (1970, 1971) through signals (1981, 1982) transferred to a computer (1983).

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