Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F7/00—Vibration-dampers; Shock-absorbers
  • F16F7/08—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other
  • F16F7/09—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other in dampers of the cylinder-and-piston type
  • F16F7/095—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other in dampers of the cylinder-and-piston type frictional elements brought into engagement by movement along a surface oblique to the axis of the cylinder, e.g. interaction of wedge-shaped elements
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
  • F04B53/14—Pistons, piston-rods or piston-rod connections
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
  • F04B53/14—Pistons, piston-rods or piston-rod connections
  • F04B53/143—Sealing provided on the piston
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
  • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
  • F04B53/162—Adaptations of cylinders
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F7/00—Vibration-dampers; Shock-absorbers
  • F16F7/08—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other
  • F16F7/09—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other in dampers of the cylinder-and-piston type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
  • F16F9/32—Details
  • F16F9/3207—Constructional features
  • F16F9/3214—Constructional features of pistons
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J1/00—Pistons; Trunk pistons; Plungers
  • F16J1/005—Pistons; Trunk pistons; Plungers obtained by assembling several pieces
  • F16J1/006—Pistons; Trunk pistons; Plungers obtained by assembling several pieces of different materials
  • F16J1/008—Pistons; Trunk pistons; Plungers obtained by assembling several pieces of different materials with sealing lips
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J10/00—Engine or like cylinders; Features of hollow, e.g. cylindrical, bodies in general
  • F16J10/02—Cylinders designed to receive moving pistons or plungers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/46—Sealings with packing ring expanded or pressed into place by fluid pressure, e.g. inflatable packings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/56—Other sealings for reciprocating rods
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
  • F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
  • F16F9/061—Mono-tubular units
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
  • F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
  • F16F9/063—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid comprising a hollow piston rod
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
  • F16F9/32—Details
  • F16F9/3207—Constructional features
  • F16F9/3235—Constructional features of cylinders

Definitions

• a piston-chamber combination comprising an elongate chamber which is bounded by an inner chamber wall and comprising a piston in said chamber to be sealingly movable relative to said chamber at least between first and second longitudinal positions of said chamber, said chamber having cross-sections of different cross-sectional areas and different circumpherential lengths at the first and second longitudinal positions of said chamber and at least substantially continuously different cross-sectional areas and different circumpherential length at intermediate longitudinal positions between the first and second longitudinal positions thereof, the cross-sectional area at the first longitudinal position being larger than the cross-sectional area at the second longitudinal position, said piston comprising an container having an elastically deformable container wall for sealing contact on the inner chamber wall, said container being elastically deformable and being inflatable to provide for different cross-sectional areas and circumferential lengths of the piston for adaptation to said different cross-sectional areas and different circumpherential lengths of said chamber during the relative movements of said piston between the first and second longitudinal positions through said intermediate longitudinal positions of said chamber.
• Inflation valves which are mentioned are valves which enable inflation of a certain enclosed volume, and these may be the Dunlop-Woods valve, the Sclaverand valve and the Schrader valve. These are in use for inflation of closed chambers, e.g. tyres of vehicles.
• the last two mentioned valve types have a spring-force operated valve core pin, and may be opened by depressing this pin for inflation and deflation of the chamber. Depressing the valve core pin may be done by manual activating, by a pressure of a fluid or by a device such as an activating pin or a valve actuator.
• the first two mentioned valve types may be opened by the pressure of a fluid alone, while the last mentioned one best may be opened by a device, as otherwise a high pressure may be needed to depress the pin.
• This invention deals with solutions for the problem of obtaining a friction force low enough to at least avoid jamming between a piston, specifically a piston comprising a container having an elastically deformable container wall, and the wall of an elongate chamber during the stroke, the chamber having different sizes of cross-sectional area's in its longitudinal direction, specifically those having different circumpherential length's, when the piston is sealingly movable relative to said chamber.
• a problem with embodiments of Figs. 6, 8 and 9 - 12 (incl.) of WO 00/70227 may be that the piston may jam in the smaller cross-sections of the chamber having cross-sections with different circumpherential sizes. Jamming may occur due to high frictional forces of the material of the wall of the pistons. These forces may mainly be created by the compression of the material(s) of the wall of the piston when the piston is moving from a first longitudinal position in the chamber having the biggest cross-sectional area to a second longitudinal position where the cross-sectional area and the circumpherential size is smaller.
• a further problem may be that embodiments of pistons comprising a container of WO 00/70227 may leak their fluid, and thus may change their sealing capability.
• the sealing force is created by internal pressure, leakage may be an important problem.
• the invention relates to a combination of a piston and a chamber, wherein: the container is made to be elastically expandable and to have its circumpherical length in the stressfree and undeformed state of its production size approximately the circumpherential length of the inner chamber wall of the container at said second longitudinal position.
• 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 approximately 50% of the first cross-sectional area.
• One such technology is one wherein the piston comprises a container comprising a deformable material.
• 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 part thereof, may be compressible, such as gas or a mixture of water and gas, or it may be at least substantially incompressible.
• the deformable material may also be spring-force operated devices, such as springs.
• the container may be adjustable to provide sealing to the wall of the chamber having different cross-sectional area's and different circumpherential sizes.
• a pressure level of a certain size depends on the difference in circumpherential length of the cross sections, and on the possibility to get a suitable sealing at the cross section with the smallest circumpherential length. If the difference is big, and the appropriate pressure level too high to obtain a suitable sealing force at the smallest circumpherential length, than change of the pressure may be arranged during the stroke. This calls for a pressure management of the piston. As commercially used materials are normally not tight, specifically when quite high pressures may be used, there must be a possibility to keep this pressure, e.g.
• the container may change.
• the container may have a first shape at the first longitudinal direction and a second shape at the second longitudinal direction, the first shape may be different from the second shape.
• the piston may comprise an enclosed space communicating with the deformable container, said enclosed space having a variable volume. In that manner, that the enclosed space may take up or release fluid when the deformable container changes volume.
• the change of the volume of the container is by that automatically adjustable. It may result in that the pressure in the container remains constant during the stroke.
• the enclosed space may comprise a spring-biased piston.
• This spring may define the pressure in the piston.
• the volume of the enclosed space may be varied. In that manner, the overall pressure or maximum/minimum pressure of the container may be altered.
• the spaces When the enclosed space is updivided into a first and a second enclosed space, the spaces further comprising means for defining the volume of the first enclosed space so that the pressure of fluid in the first enclosed space may relate to the pressure in the second enclosed space.
• the last mentioned space may be inflatable e.g. by means of a valve, preferably an inflation valve, such as a Schrader valve.
• a possible pressure drop in the container due to leakage e.g. through the wall of the container may be balanced by inflation of the second enclosed space through the defining means.
• the defining means may be a pair of pistons, one in each enclosed space.
• the defining means may be adapted to define the pressure in the first enclosed space and in the container at least substantially constant during the stroke.
• any kind of pressure level in the container may be defined by the defining means: e.g. a pressure raise may be necessary when the wall of the container expands when the piston moves to such a big cross- sectional area at the first longitudinal position that the contact area and/or contact pressure at the present pressure value may become too little, in order to maintain a suitable sealing
• defining means may be a pair of pistons, one in each enclosed space.
• the second enclosed space may be inflated to a certain pressure level, so that a pressure raise may be communicated to the first enclosed space and the container, despite the fact that the volume of the container and thus the second enclosed space may become bigger as well.
• This may be achieved by e.g. a combination of a piston and a chamber (the second enclosed space) with different cross-sectional area's in the piston rod.
• a pressure drop may also be designable.
• Pressure management of the piston may also be achieved by relating the pressure of fluid in the enclosed space with the pressure of fluid in the chamber.
• a simple manner would be to have the defining means adapted to define the pressure in the enclosed space to raise when the container is moving from the second longitudinal position to the first longitudinal position. In this situation, a simple piston between the two pressures may be provided (in order to not loose any of the fluid in the deformable container).
• this piston may define any relation between the pressures in that the chamber in which the piston translates may taper in the same manner as the main chamber of the combination.
• a device which is transportable directly from the piston rod into the container may also change the volume and/or the pressure in the container.
• the piston does not have or communicate (closed system) or does have or communicate with a valve for inflation.
• the fluid may be non-permeable for the material of the wall of the container.
• a step in the mounting process may than be that the volume of the container is permanently closed, after having put the fluid in the volume of the piston, and after having been positioned at the second longitudinal position of the chamber.
• the obtainable velocity of the piston may depend on the possibility for a big fluid flow without too much friction to and from the first closed chamber.
• the wall of the container may be permeable for the fluid.
• the container may be inflated by a pressure source which is comprised in the piston. Or an external pressure source, like one outside the combination and/or when the chamber is the source itself. All solutions demand a valve communicating with the piston.
• This valve may preferably an inflation valve, best a Schrader valve or in general, a valve with a spring force operated valve core.
• the Schrader valve has a spring biased valve core pin and closes independant of the pressure in the piston, and all kinds of fluids may flow through it. It may however also be another valve type, e.g. a check valve.
• the container may be inflated through an enclosed space where the spring-biased tuning piston operates as a check valve.
• the fluid may flow through longitudinal ducts in the bearing of the piston rod of the spring biased piston, from a pressure source, e.g. an external pressure source or e.g. an internal pressure container.
• a pressure source e.g. an external pressure source or e.g. an internal pressure container.
• the inflation may be done with the chamber as the pressure source, as the second enclosed space may prohibit inflation through it to the first enclosed space.
• the chamber may have an inlet valve in the foot of the chamber.
• an inflation valve e.g. a valve with a spring-force operated valve core such as a Schrader valve may be used, together with an actuator.
• This may be an activating pin according to WO 96/10903 or WO 97/43570, or a valve actuator according to WO99/26002 or US 5,094,263.
• the core pin of the valve is moving towards the chamber when closing.
• the activating pins from the above cited WO-documents have the advantage that the force to open the spring-force operated valve core is so low, that inflation may be easily done by a manually operated pump.
• the actuator cited in the US-patent may need the force of a normal compressor.
• the piston When the working pressure in the chamber is higher than the pressure in the piston, the piston may be inflated automatically. When the working pressure in the chamber is lower than the pressure in the piston than it is necessary to obtain a higher pressure by e.g. temporary closing the outlet valve in the foot of the chamber.
• the valve is e.g. a Schrader valve which may be opened by means of a valve actuator according to WO 99/26002, this may be achieved by creating a bypass in the form of a channel by connecting the chamber and the space between the valve actuator and the core pin of the valve. This bypass may be openened (the Schrader valve may remain closed) and closed (the Schrader valve may open) and may be accomplished by e.g. a movable piston.
• This piston may be arranged manually e.g. by a pedal, which is turning around an axle by an operator from an inactive position to an active position and vice versa. It may also be achieved by other means like an actuator, initiated by the result of a pressure measurement in the chamber and/or the container.
• Obtaining the predetermined pressure in the container may be achieved manually - the operator being informed by a pressure gauge e.g. a manometer which is measuring the pressure in the container. It may also be achieved automatically, e.g. by a release valve in the container which releases the fluid when the pressure of the fluid exceeds the maximum pressure set. It may also be achieved by a spring-force operated cap which closes the channel from the pressure source above the valve actuator when the pressure exceeds a certain pre-determined pressure value.
• a pressure measurement may be necessary in the container, which may steer an actuator which is opening and closing the bypass of the valve actuator according to WO 99/26002 of e.g. a Schrader valve of the container at a pre-determined pressure value.
• One such technology is one wherein the piston comprises a container comprising an elastically deformable container wall.
• Expansion or contraction of the container wall which is initiated by the changing size of the circumpherential length of a cross-section may be enabled by choosing a reinforcement which forces the wall of the container to expand or contract in 3 dimensions. Therefore, no surplus material between the wall of the container and the wall of the chamber will remain.
• the reinforcement of the wall of the container may be and/or may be not positioned in the wall of the container.
• a reinforcement in the wall of the container may be made of a textile material. It may be one layer, but preferably at least two layers which cross each other, so that the reinforcement may be easier to mount.
• the layers may e.g. be woven or knitted. As the woven threads lay in different layers closely to each other, the threads may be made of an elastic material.
• the layers may be vulcanized within e.g. two layers of elastic material, e.g. rubber.
• the sealing of the wall of the container to the wall of the chamber may be established by pressurizing the container to a certain pressure. Hereby will the threads being expanded a little bit so that the stitch size becomes a little bit larger.
• the contact of the wall of the container prohibit the internal pressure to expand the container in such a way that the contact length will become too large, and avoids by that jamming.
• a knitted reinforcement may be e.g. made of an elastic thread and/or elastically bendable thread.
• the expansion of the wall of the container may be made by stretching the bended loops of the knittings. The stretched loops may become back to its undeformed state when the wall of the container contracts.
• a textile reinforcement may be produced on a production line where the woven or knitted textile reinforcement lay as a cylinder within two layers of elastic material. Within the smallest cylinder a bar is positioned on which caps are being held in a sequence top-down-top-down etc. and these may move on that bar. At the end of the line an vulcanisation oven is being held. The inside of the oven may have the size and the form of the container in a stressfree and underformed state. The part of the cylinders being inside the oven is being cut on length, two caps being positioned within the cylinders at both ends, and being kept there. The oven is closed, and steam of over 100°C and high pressure is put in. After approx.
• the oven may be opened and the ready produced container wall with the two caps vulcanised in that wall.
• the minutes lead time of the vulcanisation there may more than one oven, e.g. rotating or translating, and all ending at the end of the production line. It may also be possible to have more than one oven on the production line itself, using the transport lead time as the vulcanisation time.
• the reinforced fibers may be produced by e.g. injection moulding, incl. an assembling socket ⁇ r by cutting a string, which thereafter is being put at both ends onto assembling socket. Both options may easily series produced. For the rest will the production process be analogeous with the above mentioned ones rearding the textile reinforcement.
• the piston comprising an elastically deformable container may also comprise reinforcement means which are not positioned in the wall, e.g. a plurality of elastic arms, which may or may not be inflatable, connected to the wall of the container.
• reinforcement means which are not positioned in the wall, e.g. a plurality of elastic arms, which may or may not be inflatable, connected to the wall of the container.
• the reinforcement functions also to limit the deformation of the wall of the container due to the pressure, in the chamber.
• Another option is a reinforcement outside the wall of the container.
• Another aspect of the invention is one relating to a combination of a piston and a chamber, wherein: the chamber defines an elongate chamber having a longitudinal axis, the piston being movable in the chamber at least from a second longitudinal position to a first longitudinal position, the chamber having an elastically deformable inner wall along at least part of the inner chamber wall between the first and second longitudinal positions, - the chamber having, at a first longitudinal position thereof when the piston is positioned at that position, a first cross-sectional area thereof and, at a second longitudinal position thereof when the piston is positioned at that position, a second cross-sectional area, the first cross-sectional area being larger than the second cross-sectional area, the change in cross-section of the chamber being at least substantially continuous between the first and second longitudinal positions when the piston is moved between the first and second longitudinal positions.
• this aspect relates to a chamber having adapting capabilities.
• the piston may be made of an at least substantially incompressible material - or a combination may be made of the adapting chamber and an adapting piston - such as a piston according to the above aspects.
• the piston has, in a cross section along the longitudinal axis, a shape tapering in a direction from to the second longitudinal positions.
• a preferred manner of providing an adapting chamber is to have the chamber comprise: an outer supporting structure enclosing the inner wall and a fluid held by a space defined by the outer supporting structure and the inner wall.
• the choice of fluid or a combination of fluids may help defining the properties of the chamber, such as the sealing between the wall and the piston as well as the force required etc.
• the invention relates to a combination of a piston and a chamber, wherein:
• the chamber defines an elongate chamber having a longitudinal axis
• the chamber having, at a first longitudinal position thereof, a first cross-sectional shape and area thereof and, at a second longitudinal position thereof, a second cross-sectional shape and . area, 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 and second longitudinal positions,
• the piston being adapted to adapt itself to the cross-section of the chamber when moving from the first to the second longitudinal position of the chamber.
• This very interesting aspect is based on the fact that different shapes of e.g. a geometrical figure have varying relations between the circumference and the area thereof. Also, changing between two shapes may take place in a continuous manner so that the chamber may have one cross-sectional shape at one longitudinal position thereof and another at a second longitudinal position while maintaining the preferred smooth variations of the surface in the chamber.
• the shape of a cross-section is the overall shape thereof - notwithstanding the size thereof. Two circles have the same shape even though one has a diameter different from that of the other.
• the first cross-sectional area is at least 2%, such 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%, such at least 95 % larger than the second cross-sectional area.
• the first cross-sectional shape is at least substantially circular and wherein the second cross-sectional shape is elongate, such as oval, having a first dimension being at least 2, such as at least 3, preferably at least 4 times a dimension at an angle to the first dimension.
• the first cross-sectional shape is at least substantially circular and wherein the second cross-sectional shape comprises two or more at least substantially elongate, such as lobe-shaped, parts.
• a first circumference of the chamber is 80-120%, such as 85-115%, preferably 90-110, such as 95-105, preferably 98-102% of a second circumference of the chamber in the cross-section at the second longitudinal direction
• problems may arise when attempting to seal against a wall having varying dimensions due to the fact that the sealing material should both provide a sufficient sealing and change its dimensions. If, as is the situation in the preferred embodiment, the circumference changes only to a small degree, the sealing may be controlled more easily.
• the first and second circumferences are at least substantially identical so that the sealing material is only bent and not stretched to any significant degree.
• the circumference may be desired to change slightly in that when bending or deforming a sealing material, e.g. a bending will cause one side thereof to be compressed and another stretched. Overall, it is desired to provide the desired shape with a circumference at least close to that which the sealing material would automatically "choose".
• One type of piston which may be used in this type of combination, is the one comprising a piston comprising a deformable container.
• the container may be elastically or non-elastically deformable. In the last way the wall of the container may bent while moving in the chamber.
• Elastically deformable containers with a production size approximately the size of the circumpherencial length of the first longitudinal position of the chamber, having a reinforcement type which allows contraction with high frictional forces may also be used in this type of combination, and may be specifically with high velocities of the piston.
• Elastically deformable containers with a production size approximately the size of the circumpherencial length of the second longitudinal position of the chamber, having a reinforcement type of the skin which allows parts of the wall of the container having different distances from the central axis of the chamber in a longitudinal cross-section of the chamber may also be used.
• one of the piston and the chamber may be stationary and the other moving - or both may be moving. This has no impact on the functionning of the combination.
• the piston may also slide over an internal and an external wall.
• the internal wall may have a taper form, while the external wall is cylindrical.
• the present combination may be used for a number of purposes in that it primarily focuses on a novel manner of providing an additional manner of tailoring translation of a piston to the force required/taken up.
• the area/shape of the cross-section may be varied along the length of the chamber in order to adapt the combination for specific purposes and/or forces.
• One purpose is to provide a pump for use by women or teenagers - a pump that nevertheless should be able to provide a certain pressure. In that situation, an ergonomically improved pump may be required by determining the force which the person may provide at which position of the piston - and thereby provide a chamber with a suitable cross-sectional area/shape.
• Another use of the combination would be for a shock absorber where the area/shape would determine what translation a certain shock (force) would require. Also, an actuator may be provided where the amount of fluid introduced into the chamber will provide differing translation of the piston depending on the actual position of the piston prior to the introducing of the fluid.
• the nature of the piston, the relative positions of the first and the second longitudinal positions and the arrangement of any valves connected to the chamber may provide pumps, motors, actuators, shock absorbers etc. with different pressure characteristics and different force characteristics.
• a medium may be sucted into a chamber which may thereafter be closed by a valve arrangement.
• the medium may be compressed by the movement of the chamber and/or the piston and thereafter a valve may release this compressed medium from the chamber.
• a medium may be pressed into a chamber by a valve arrangement and the piston and/or the chamber may be moving, initiating the movement of an attached device.
• the chamber may be completely closed, wherein a compressable medium may be compressed by the movement of the chamber and/or the piston.
• a non-compressable medium may be positioned inside the chamber, e.g. the piston may be equipeed by several small channels which may give a dynamic friction, so that the movement may be slowed down.
• the invention may also be used in propulsion applications where a medium may be used to move a piston and/or a chamber, which may turn around an axis as e.g. in a motor. Any kind of The principles according this invention may be applicable on all above mentioned applications.
• the invention 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 entrance connected to the chamber and comprising a valve means, and a fluid exit connected to the chamber.
• the engaging means may 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.
• a pump of this type is preferred when a pressurised fluid is desired.
• the engaging 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.
• a pump of this type is preferred when no substantial pressure is desired but merely transport of the fluid.
• the largest force may, ergonomically, be provided at the lowest position of the piston/engaging means/handle.
• the smallest cross-sectional area may be desired shortly before the lowest position of the engaging means in order for the resulting pressure to open the valve and a larger cross-sectional area to force more fluid into the tyre.
• the pump according to the invention may use substantial less working force than comparable pumps based on the traditional piston-cylinder combination, e.g. water pumps may extraxt water from greater depths. This feature is of great significance e.g. in underdeveloped countries.
• the chamber according to the invention may have another function. It may comply to the physical needs (ergonomical) of the user by a proper design of the chamber, e.g. as if there existed a pressure difference: e.g. according to Figs. 17B and 17A respectively. This may also be accomplished by the use of valves.
• the invention also relates to a piston which seals to a cylinder, and at the same time to a tapered cylinder.
• the piston may or may not comprise an elastically deformable container.
• the resulting chamber may be of the type where the cross-sectional area's have different circumpherential sizes or that these may be identical.
• the piston may comprise one of more piston rods.
• the cylinder at the outside may be cylindrical or tapered as well.
• the invention relates to a shock absorber comprising: a combination according to any of the combination aspects, means for engaging the piston from a position outside the chamber, wherein the engaging means 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.
• the absorber may further comprise a fluid entrance connected to the chamber and comprising a valve means.
• the absorber may comprise a fluid exit connected to the chamber and comprising a valve means.
• the chamber and the piston forms an at least substantially sealed cavity comprising a fluid, the fluid being compressed when the piston moves from the first to the second longitudinal positions.
• the absorber would comprise means for biasing the piston toward the first longitudinal position.
• the invention relates to an actuator comprising: a combination according to any of the combination aspects, means for engaging the piston from a position outside the chamber, means for introducing fluid into the chamber in order to displace the piston between the first and the second longitudinal positions.
• the actuator may comprise a fluid entrance connected to the chamber and comprising a valve means.
• a fluid exit connected to the chamber and comprising a valve means may be provided.
• the actuator may comprise means for biasing the piston toward the first or second longitudinal position.
• the invention relates to a motor comprising - a combination according to any of the above mentioned combination aspects.
• the invention also relates to a power unit, which preferably may be movable, e.g. by parachute - a M(ovable) P(ower) U(nit).
• a power unit may comprise a power source of any kind, preferably at least one set of solar sells, and a power device, e.g. a motor according to the invention.
• Fig. 1A shows a longitudinal cross-section of a non-moving piston in a non- pressurized cylinder at the first longitudinal position - the piston is shown in its production size, and when pressurized.
• Fig. IB shows the contact pressure of the pressurized piston of Fig. 1A on the wall of the cylinder.
• Fig. 2A shows a longitudinal cross-section of the piston of Fig. 1A in a cylinder at the first (right) and second (left) longitudinal position, the piston is non-pressurized.
• Fig. 2B shows the contact pressure of the piston of Fig. 2A on the wall of the cylinder at the second longitudinal position.
• Fig. 2C shows a longitudinal cross-section of the piston of Fig. 1 A in a cylinder at the second longitudinal position, the piston is pressurized on the same pressure level as the one of Fig. 1A - also is shown the piston at the first longitudinal position (production) size.
• Fig. 2D shows the contact pressure of the piston of Fig. 2C on the wall of the cylinder at the second longitudinal position.
• Fig. 3 A shows a longitudinal cross-section of a piston of Fig. 1A in a cylinder at the first longitudinal position shown in its production size, and pressurized while the piston is subjected to a pressure in the chamber.
• Fig. 3B shows the contact pressure of the piston of Fig. 3 A on the wall of the cylinder.
• Fig. 4A shows a longitudinal cross-section of a non-moving piston according to the invention in a non-pressurized cylinder at the second longitudinal position, shown in its production size, and when pressurized to a certain level.
• Fig. 4B shows the contact pressure of the pressurized piston of Fig. 4 A on the wall of the cylinder.
• Fig. 4C shows a longitudinal cross-section of a non-moving piston according to the invention in a cylinder at the second longitudinal position, shown in its production size, and at the first longitudinal position when pressurized to the same level as that of Fig. 4A.
• Fig. 4D shows the contact pressure of the piston of Fig.
• Fig. 5 A shows a longitudinal cross-section of the piston of Fig. 4A in a non- pressurized cylinder at the second longitudinal position, the piston with its production size, and when pressurized.
• Fig. 5B shows the contact pressure of the pressurized piston of Fig. 5A on the wall of the cylinder.
• Fig. 5C shows a longitudinal cross-section of the piston of Fig. 4A in a cylinder at the second longitudinal position, the piston with its production size, and when pressurized, subjected to a pressure from the cylinder.
• Fig. 5D shows the contact pressure of the piston of Fig. 5C on the wall of the cylinder.
• FIG. 6 A shows a longitudinal cross-section of a chamber with fixed different areas of the transversal cross-sections and a first embodiment of the piston comprising a textile reinforcement with radially-axially changing dimensions during the stroke - the piston arrangement is shown at the beginning, and at the end of a stroke - pressurized - where it has unpressurized its production size.
• Fig. 6B shows an enlargement of the piston of Fig. 6 A at the beginning of a stroke.
• Fig. 6C shows an enlargement of the piston of Fig. 6A at the end of a stroke.
• Fig. 6D shows a 3-dimensional drawing of a reinforcement matrix of an elastic textile material, positioned in the wall of the container when the container is to be expanded
• Fig. 6E shows the pattern of Fig. 6D when the wall of the container has been expanded
• Fig. 6F shows a 3-dimensional drawing of a reinforcement pattern of an inelastic textile material, positioned in the wall of the container when the piston is to be expanded
• Fig. 6G shows the pattern of Fig. 6F when the wall of the container has been expanded
• Fig. 6H shows production details of a piston with a textile reinforcement.
• Fig. 7 A shows a longitudinal cross-section of a chamber with fixed different areas of the transversal cross-sections and a second embodiment of the piston comprising a fiber reinforcement ('Trellis Effect') with radially- axially changing dimensions of the elastic material of the wall during the stroke - the piston arrangement is shown at the beginning, and at the end of a stroke - pressurized - where it has unpressurized its production size.
• Fig. 7B shows an enlargement of the piston of Fig. 7 A at the beginning of a stroke.
• Fig. 7C shows an enlargement of the piston of Fig. 7A at the end of a stroke.
• Fig. 8 A shows a longitudinal cross-section of a chamber with fixed different areas of the transversal cross-sections having different circumpherical length
• a third embodiment of the piston comprising a fiber reinforcement (no 'Trellis Effect') with radially-axially changing dimensions of the elastic material of the wall during the stroke - the piston arrangement is shown at the first longitudinal position, and at the second longitudinal position - pressurized - where it has unpressurized its production size.
• Fig. 8B shows an enlargement of the piston of Fig. 8 A at the beginning of a stroke.
• Fig. 8C shows an enlargement of the piston of Fig. 8 A at the end of a stroke.
• Fig. 8D shows a top view of the piston of Fig. 8 A with a reinforcement in the wall in planes through the central axis of the piston - left: at the first longitudinal position, right: at the second longitudinal position.
• Fig. 8E shows a top view of the piston alike the one of Fig. 8 A with a reinforcement in the wall in planes partly through the central axis and partly outside the central axis of the piston - left: at the first longitudinal position, right: at the second longitudinal position.
• Fig. 8F shows a top view of the piston alike the one of Fig. 8A with a reinforcement in the wall in planes not through the central axis of the piston - left: at the first longitudinal position, right: at the second longitudinal position.
• Fig. 8G shows production details of a piston with a fiber reinforcement.
• Fig. 9 A shows a longitudinal cross-section of a chamber with fixed different areas of the transversal cross-sections having different circumpherical length and a fourth embodiment of the piston comprising an "octopus" device, limiting stretching of the container wall by tentacles, which may be inflatable - the piston arrangement is shown at the first longitudinal position of the chamber, and at the second longitudinal position of the chamber - presssurized - where it has unpressurized its production size.
• Fig. 9B shows an enlargement of the piston of Fig. 9A at the first longitudinal position of the chamber.
• Fig. 9C shows an enlargement of the piston of Fig. 9 A at the second longitudinal postion of the chamber.
• Fig. 10A shows the embodiment of Fig. 6 where the pressure inside the piston may be changed by inflation through e.g. a Schrader valve which is positioned in the handle and/or e.g. a check valve in the piston rod, and where an enclosed space is balancing the change in volume of the piston during the stroke.
• a Schrader valve which is positioned in the handle and/or e.g. a check valve in the piston rod
• Fig. 10B shows instead of an inflation valve, a bushing enabling connection to an external pressure source.
• Fig. IOC shows details of the guidance of the rod of the check valve.
• Fig. 10D shows the flexible piston of the check valve in the piston rod.
• Fig. 10E shows the embodiment of Fig. 6, where the volume of the enclosed space of Fig. 10A-D has been exchangend by a pressure source and an inlet valve for inflating the piston from the pressure source, and an outlet valve for pressure releave to the pressure source - enlarged details of the valve- valve actuator combinations according to Fig. 11D.
• Fig. 10F shows the embodiment of Fig. 10E, where there are steerable valves and a jet or a nozzle - shown as black boxes.
• Fig. IIA shows the embodiment of Fig. 6 where the pressure inside the piston may be maintained constant during the stroke and where a second enclosed space may be inflated through a Schrader valve which is positioned in the handle, communicating with the first enclosed space through a piston arrangement - the piston may be inflated by a Schrader valve + valve actuator arrangement with the pressure of the chamber as pressure source, while the outlet valve of the chamber may be manually controlled by a turnable pedal.
• Fig. 11B shows a piston arrangement and its bearing where the piston arrangement is communicating between the second and the first enclosed space.
• Fig. 11C shows a alternative piston arrangement adapting itself to the changing cross-sectional area's in its longitudinal direction inside the piston rod.
• Fig. 11D shows an enlargement of the inflation arrangement of the piston of Fig.
• FIG. 11A shows an end of the stroke.
• Fig. HE shows an enlargment of the bypass arrangement for the valve actuator for closing and opening of the outlet valve.
• Fig. 11F shows an enlargement of an automatic closing and opening arrangement of the outlet valve - a comparable system is shown for optaining a predetermined pressure value in the piston (dashed).
• Fig. 11G shows an enlargement of an inflation arrangement of the piston of Fig.
• Fig. 11H shows an alternative solution for the one of Fig. 11G, comprising a combination of a valve actuator and a spring positioned below the piston of the valve actuator.
• Fig. 12 shows an arrangement where the pressure in the container may depend of the pressure in the chamber.
• Fig. 13 A shows a longitudinal cross-section of a chamber with an elastical or flexible wall having different areas of the transversal cross-sections and a piston with fixed geometrical sizes - the arrangement of the combination is shown at the beginning and at the end of the pump stroke.
• Fig. 13B shows an enlargement of the arrangement of the combination at the beginning of a pump stroke.
• Fig. 13C shows an enlargement of the arrangement of the combination during a pump stroke.
• Fig. 13D shows an enlargement of the arrangement of the combination at the end of a pump stroke.
• Fig. 14 shows a longitudinal cross-section of a chamber having an elastical or flexible wall with different areas of the transversal cross-sections and a piston with variable geometrical sizes - the arrangement of the combination is shown at the beginning, during and at the end of the stroke.
• Fig. 15A shows examples of transversal cross-sections made by Fourier Series Expansions of a pressurizing chamber of which the transversal cross- sectional area decreases, while the circumpherical size remains constant.
• Fig. 15B shows a variant of the pressurizing chamber of Fig. 7A, which has now a longitudinal cross-section with fixed transversal cross-sections which are designed in such a way that the area decreases while the circumference of it approximately remains constant or decreases in a lower degree during a pump stroke.
• Fig. 15C shows transversal cross-section G-G (dotted lines) and H-H of the longitudinal cross section of Fig. 15B.
• Fig. 15D shows transversal cross-section G-G (dotted lines) and I-I of the longitudinal cross section of Fig. 15C.
• Fig. 15E shows other examples of transversal cross-sections made by Fourier
• Fig. 15F shows an example of an optimized convex shape of the transversal cross section under certain contraints.
• Fig- 16 shows a combination where the piston in moving in a cylinder over a tapered center.
• F Fiigg.. 1 177AA shows an ergonomical optimized chamber for pumping purposes and manual operation.
• Fig. 17B shows the corresponding force-stroke diagram.
• Fig. 18A shows an example of a Movable Power Unit, hanging under a parachute.
• Fig. 18B shows details of the Movable Power Unit.
• Fig. 1A shows the longitudinal cross-section of a non-moving non-pressurized piston 5 at the first longitudinal position of a non-pressurized chamber 1, having at that position a circular cross-sections with a constant radius.
• the piston 5 may have a production size approximately the diameter of the chamber 1 at this first longitudinal position.
• the piston 5* when pressurized to a certain pressure level is shown.
• the pressure inside the piston 5* results in a certain contact length.
• Fig. IB shows the contact pressure of the piston 5* of Fig. 1A.
• the piston 5* may jam at this longitudinal position.
• Fig. 2 A shows the longitudinal cross-section of a non-moving non-pressurized piston 5 at the first longitudinal position and the piston 5' at the second longitudinal position of a non- pressurized chamber 1, the chamber having circular cross-sections with a constant radius at both the first and second longitudinal positions.
• the piston 5 may have a production size approximately the diameter of the chamber 1 at this first longitudinal position.
• the piston 5' shows the piston 5, non- pressurized positioned into the smaller cross-section of the second longitudinal position.
• Fig. 2B shows the contact pressure of the piston 5' on the wall of the chamber at the second longitudinal position.
• the piston 5' may jam at this longitudinal position.
• Fig. 2C shows the longitudinal cross-section of a non-moving non-pressurized piston 5 at the first longitudinal position and the piston 5' at the second position of a non-pressurized chamber 1, the chamber having circular cross-sections with a constant radius at both the first and second longitudinal positions.
• the piston 5 may have a production size approximately the diameter of the chamber 1 at this first longitudinal position.
• the piston 5'* shows the piston 5, pressurized to the same level as the one of Fig. 1A, positioned into the smaller cross-section of the second longitudinal position.
• Fig. 2D shows the contact pressure of the piston 5'* on the wall of the chamber at the second longitudinal position.
• the piston 5'* may jam at this longitudinal position: the friction force may be 72 kg.
• Fig. 3A shows the piston 5 of Fig. 1A, and the deformed piston 5"* when pressurized to the same pressure level of that of piston 5* of Fig. 1A.
• the deformation is caused by the pressure in the chamber 1*, when the piston may not have means to limit the stretching, which is mainly in the meridian (longitudinal direction of the chamber) direction.
• Fig. 3B shows the contact pressure.
• the piston 5" * may jam at this longitudinal position.
• Fig. 4A shows the longitudinal cross-section of a piston 15 at the second longitudinal position of a non-pressurized chamber 10, having a circular cross-section.
• the piston 15 may have a production size approximately the diameter of the chamber 10 at this second longitudinal position.
• Piston 15'* shows the deformed piston 15 pressurized to a certain level. The deformation is due to the fact that the Young's modulus in the hoop direction (in a cross-sectional plane of the chamber) is choosen lower than that in the meridian direction (in the longitudinal direction of the chamber).
• Fig. 4B shows the contact pressure on the wall of piston 15'*. This results in an appropriate friction force (4.2 kg), and suitable sealing.
• Fig. 4C shows the longitudinal cross-section of piston 15 at the second longitudinal position (production size) of the non-pressurized chamber 10, and when pressurized 15"* at the first longitudinal position - the piston 15"* may have the same pressure as when the piston 15'* is positioned at the second longitudinal position of the chamber 10 (fig. 4A). Also here is the deformation in the hoop- and meridian direction different.
• Fig. 4D shows the contact pressure on the wall of piston 15"*. This results in an appropriate friction force (0.7 kg) and a suitable sealing.
• FIG. 5A shows the longitudinal cross-section of the piston 15 (production size) and the piston 15'* at the second longitudinal position of the non-pressurized chamber 10.
• the piston 15'* is showing the deformed structure of piston 15 when the piston 15 is pressurized.
• the piston 15, 15'* have been attached at the lower end to an imaginair piston rod in order to prevent piston movement during application of the chamber pressure.
• Fig. 5B shows the contact pressure of the piston 15'* of Fig. 5A. This is low enough to allow movement (friction force 4.2 kg) and suitable for sealing.
• Fig. 5C shows the longitudinal cross-section of the piston 15 (production size) and 15"* pressurized and deformed by the chamber pressure at the second longitudinal position of the pressurized chamber 10*.
• the piston 15, 15'* have been attached at the lower end to an imaginair piston rod in order to prevent piston movement during the application of the chamber pressure.
• the deformed piston 15"* is approximately twice as long as the undeformed piston 15.
• Fig. 5D shows the contact pressure of the piston 15"* of Fig. 5C. This is low enough to allow movement (friction force 3.2 kg) and suitable for sealing.
• a chamber pressure on a piston comprising a pressurized elastically deformable container
• the stretching due to the applied chamber force is big and it may be necessary to limit this.
• Fig. 6-9 deal with the limitation of the stretching of the skin of the piston, which may result in a contact area small enough to enable appropriate sealing and a friction force low enough to enable movement of the piston.
• This comprises a limitation of the stretching in the longitudinal direction when the container may or may not be subjected to a pressure in the chamber, and to allow expansion in the transversal direction, when moving from the second to the first longitudinal position of the chamber, and specifically allow contraction when moving the other way around.
• the stretching in the longitudinal direction of the wall of the container-type piston may be limited by several methods. It may be done by a reinforcement of the wall of the container by using e.g. textile and/or fiber reinforcement. It may also be done by an inside the chamber of the container positioned expanding body with a limitation for its expansion, while it is connected to the wall of the container. Other methods may be used, e.g. pressure management of a chamber in- between two walls of the container, pressure management of the space above the container etc. TTJhe reinforcement may also be positioned outside the piston.
• the expansion behaviour of the wall of the container may be depending on the type of the stretching limitation used.
• the keeping of the piston which is moving over the piston rod, while expanding may be guided by a mechanical stop.
• the positioning of such a stop may be depending on the use of the piston-chamber combination. This may also be the case for the guidance of the container over the piston rod, while expanding and/or sujected to external forces.
• All kinds of fluids may be used - a combination of a compressable and a non-compressable medium, a compressable medium only or a non-compressable medium only.
• the change of the size of the container may be substantial from the smallest cross- sectional area, where it has its production size, and expanded at the biggest cross-sectional area, a communication of the chamber in the container with a first enclosed space, e.g. in the piston rod may be necessary.
• the first enclosed space may be pressurized as well, also during the change of the volume of the chamber of the container. Pressure management for at least the first enclosed space may be needed.
• Fig. 6A shows a longitudinal cross-section of the chamber 186 with a concave wall 185 and an inflatable piston comprising a container 208 at the first longitudinal position in the chamber 186 and the same 208' at the second longitudinal position in the chamber 186.
• the container 208' shows its size, when pressurized, which is approximately its production size, having a textile reinforced 189 in the skin 188 of the wall 187.
• the wall 187 of the container expands until a stop arrangement, which may be the textile reinforcement 189 and/or a mechanical stop 196 outside the container 208 and/or another stop arrangement stops the movement during the stroke. And thus the expansion of the container 208.
• the first main function however of the textile reinforcement is to limit this longitudinal stretching 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 a contraction when the container is moving to the second longitudinal position (and vice versa where an expansion is necessary).
• the pressure inside the container 208,208' may remain constant. This pressure depends on the change in the volume of the container 208,208' , thus on the change in the circumpherical length of the cross-sections of the chamber 186 during the stroke. It may also be possible that the pressure changes during the stroke. It may also be possible that the pressure changes during the stroke, depending or not of the pressure in the chamber 186.
• Fig. 6B shows a first embodiment of the expanded piston 208 at the first longitudinal position of the chamber 186.
• the wall 187 of the container is build up by a skin 188 of a flexable material, which may be e.g. a rubber type or the like, with a textile reinforcement 189, which allows expansion and contraction.
• the change of the size of the piston during the stroke results not necessarily in an identical shape, as drawn. Due to the expansion the thickness of the wall of the container may be smaller than that of the container as produced when positioned at the second longitudinal position) of the chamber 186.
• An impervious layer 190 inside the wall 187 may be present.
• caps 191,192 may be able to translate and/or rotate over the piston rod 195. These movements may be done by various devices as e.g. different types of bearings which are not shown.
• the cap 191 in the top of the container may move upwards and downwards.
• the stop 196 on the piston rod 195 outside the container 208 limits the upwards movement of the container 208.
• the cap 192 in the bottom may only move downwards because the stop 197 prevent a movement upwards - this embodiment may be thought to be used in a piston chamber device which has pressure in chamber 186 beneath the piston.
• Other arrangements of stops may be possible in other pump types, such as double working pumps, vacuum pumps etc. and depends solely of the design specifications.
• Other arrangements for enabling and/or limiting the relative movement of the piston to the piston rod may occur.
• the tuning of the sealing force may comprise a combination of an incompressable fluid 205 and a compressable fluid 206 (both alone are also a possibility) inside the container, while the chamber 209 of the container may communicate with a second chamber 210 comprising a spring-force operated piston 126 inside the piston rod 195.
• the fluid(s) may freely flow through the wall 207 of the piston rod through the hole 201. It may be possible that the second chamber is communicating with a third chamber (see Fig. 12), while the pressure inside the container also may be depending on the pressure in the chamber 186.
• the container may be inflatable through the piston rod 195 and/or by communicating with the chamber 186. O-rings or the like 202, 203 in said cap in the top and in said cap in the bottom, respectively seal the caps 191,192 to the piston rod.
• the cap 204 shown as a screwed assembly at the end of the piston rod 195 thighthens said piston rod. Comparable stops may be positioned elsewhere on the piston rod, depending on the demanded movement of the wall of the container.
• Fig. 6C shows the piston of Fig. 6B at the second longitudinal position of the chamber .
• the cap 191 in the top is moved over a distance a' from the stop 196.
• the spring-force operated valve piston 126 has been moved over a distance b' .
• the bottom cap 192 is shown adjacent to the stop 197 - when there may be pressure in the chamber 186 below the piston, than the chamber 186'' , may be pressed against the stop 197.
• the compressable fluid 206' and the non-compressable fluid 205' may be pressed against the stop 197.
• Fig. 6D is a 3-dimensional drawing and shows a reinforcement matrix of textile material, allowing elastically expansion and contraction of the wall of the container 208,208' , when sealingly moving in the chamber 186.
• the textile material may be elastical, and laying in separate layers over each other.
• the layers may also lay woven in each other.
• the angle between the two layers may be different from 54°44'.
• the expansion and contraction of the wall of the container may be equal in the XYZ-direction.
• the material of the threads may be elastical, another device may be necessary to stop the expansion, such as a mechanical stop. This may be the wall of the chamber and/or a mechanical stop shown on the piston rod, as shown in Fig. 6B.
• Fig. 6E is a 3-dimensional drawing and shows the reinforcement matrix of Fig. 6D which has been expanded.
• the stitches ss' and tt' which are larger than the stitches ss and tt.
• the result of the contraction may result in the matrix shown in Fig. 6D.
• Fig. 6F is a 3-dimensional drawing and shows a reinforcement matrix of textile material which may be made of inelastic thread (but elastically bendable), and lay in separate layers over each other or knitted in each other.
• the expansion is possible because of the extra length of each loop 700, which is available, when the container is in the production size - also pressurized, when positioned at the second longitudinal position of the chamber. Stitches ss' ' and tt' ' in each direction.
• Fig. 6G is a 3-dimensional drawing and shows the reinforcement matrix of Fig. 6F which has been expanded. The stitches ss' " and tt' " which are larger than the stitches ss" and tt". The result of the contraction may result in the matrix shown in Fig. 6F.
• Fig. 6H shows three stages I, JH and III of a production process of the piston comprising an elastically deformable container.
• a rubber Clat 601 positioned, over which a reinforced It 602 e.g. according to those of Fig. 6E-G is positioned. Over the last mentioned another rubber Clat has been positioned.
• a caps 604 may be positioned between the machet 601 and the rod. All may slide over the rod 600.
• the rod 600 may be hollow and may be connected to a high pressure steam source. Stage II: the pressurized steam may enter the cave 608 of the oven 606 by outlets 605 which may be positioned at the end of the rod.
• a piece of the complete rubber/reinforcement Scits 607 may be cut and transported over the rod 600 into the cave 608.
• the cave may than be closed and pressurized steam is injected into the cave.
• Vulcanisation may take place, incl. the mounting of the wall of the container on the caps 604.
• the It may take the form of the curve.
• After vulcanisation the cave may be opened and the container which has than its production size, is pushed out (HI).
• HI In order to use the vulcanisation time of a piston to also produce other pistons several methods may be used. Bulging of the (complete: incl. textile reinforcement) rubber Scits 607 may take place before the vulcanisation.
• the rod 600 may than be updivided in several parts, each approximately the height of a container at its production size. Each may be disconnected from the main rod before entering a cave. And/or, several caves may be present at the end of the production feed line, which may each stand, receive a complete Scit 607 and vulcanize it. This may be achived by the caves rotating and/or translating to and from the end of the production feed line. It may also be possible that a number of vulcanisation caves are integrated in the production feed line.
• Fig. 7A shows a longitudinal cross-section of the chamber 186 with a concave wall 185 and an inflatable piston comprising a container 217 at the first longitudinal position of the chamber and the same 217' at the second longitudinal position.
• the container 217' shows, pressurized, approximately its production size.
• Fig. 7B shows the expanded piston 217 at the first longitudinal position of the chamber.
• the wall 218 of the container is build up by a skin 216 of an elastical material, which may be e.g. a rubber type or the like, with a fiber reinforcement 219 according to the Trellis Effect, which allows expansion of the container wall 218.
• An impervious layer 190 inside the wall 187 may be present. It may be tightly squeezed in the cap 191 in the top and the cap 192 in the bottom of the container 217,217'. Details of said caps are not shown and all kinds of assembling methods may be used - these may be capable to adapt themselves to the changing thickness of the wall of the container. Both caps 191,192 may translate and/or rotate over the piston rod 195. These movements may be done by various methods as e.g. different types of bearings which are not shown. The cap 191 in the top may move upwards and downwards until stop 214 limits this movement.
• the cap 192 in the bottom can only move downwards because the stop 197 prevent a movement upwards - this embodiment is thought to be used in a piston chamber device which has pressure in chamber 186 beneath the piston.
• Other arrangements of stops may be possible in other pump types, such as double working pumps, vacuum pumps etc. and depends solely of the design specifications.
• Other arrangements for enabling and/or limiting the relative movement of the piston to the piston rod may occur.
• the pressure inside the container 217,217' may remain constant. It may also be possible that the pressure changes during the stroke.
• the tuning of the sealing force may comprise a combination of an incompressable fluid 205 and a compressable fluid 206 (both alone are also a possibility) inside the container, while the chamber 215 of the container 217,217' may communicate with a second chamber 210 comprising a spring-force operated piston 126 inside the piston rod 195.
• the fluid(s) may freely flow through the wall 207 of the piston rod through the hole 201. It may be possible that the second chamber is communicating with a third chamber (see Fig. 10), while the pressure inside the container also may be depending on the pressure in the chamber 186.
• the container may be inflatable through the piston rod 195 and/or by communicating with the chamber 186.
• the cap 204 shown as a screwed assembly at the end of the piston rod 195 thighthens said piston rod.
• Fig. 7C shows the piston of Fig. 7B at the second longitudinal position of the chamber 186.
• the contact area 211' which is small.
• the cap 191 is moved over a distance c' from the stop 216.
• the spring-force operated valve piston 126 has been moved over a distance d' .
• the bottom cap 192 is shown adjacent to the stop 197 - if there is pressure in the chamber 186, than the 192 is pressed against the stop 197.
• the compressable fluid 206' and the non-compressable fluid 205' which may have changed volume in the container.
• Fig. 8A,B,C deal with the construction of the piston which may be identical with that of
• the reinforcement comprises of any kind of reinforcement means which may be bendable, and which may ly in a pattern of reinforcement 'colums' which do not cross each other.
• This pattern may be one of parallel to the central axis 184 of the chamber 186 or one of where a part of the reinforcement means may be in a plane through the central axis 184.
• Fig. 8A shows an inflatable piston comprising a container 228 at the first longitudinal position of the chamber 186 and the same 228' at the second longitudinal position of the chamber 186 - pressurized - where it has unpressurized its production size.
• Fig. 8B shows the container 228 at the first longitudinal position of the chamber 186.
• the wall 221 of the container comprises an elastical material 222,224 and the reinforecement means 223 e.g. a fiber.
• An impervious layer 226 may be present. The contact area between the container 228 and the wall 185 of the chamber 186.
• Fig. 8C shows the container 228' at the second longitudinal position of the chamber 186.
• the contact area 225' may be a bit larger than that of the contact area 225.
• the top cap 191 has been moving e' from the stop 214.
• Fig. 8D shows a top view of the piston 228 and 228' , respectively with the reinfor-cement means 223, and 223" respectively at the first and second longitudinal position of the chamber 186 respectively.
• Fig. 8E shows a top view of a piston alike the one of 228 and 228', respectively with an alternative embodiment of the reinforcement means 229, and 229' respectively at the first and second longitudinal position of the chamber 186 respectively. A part of the reinforcement does not ly in planes through the central axis 184 in the longitudinal direction of the chamber 186.
• Fig. 8F shows a top view of the piston alike the one of 228 and 228' with a reinforcement 227 and 227' in the wall in the wall of the container in planes not through the central axis 184 of the chamber 186. During the stroke the wall of the container turns around the central axis 184.
• Fig. 8G shows schematically how fibers 802 may be mounted in caves 801 of the cap 800. This may be achieved by rotating the cap and the fibers around the central axis 803, each may have its own velocity, while the fibers 802 are being pushed towards and in the caves 801.
• Fig. 9A shows a longitudinal cross-section of the chamber 186 with a convex wall 185 and an inflatable piston comprising a container 258 at the beginning and the same 258' at the end of a stroke.
• the pressurized container 258' at the second longitudinal position.
• Fig. 9B shows the longitudinal cross-section of the piston 258 having a reinforced skin by a plurality of at least elastically deformable support members 254 rotatably fastened to a common member 255, connected to the an skin 252 of said piston 258,258' .
• These members are in tension, and depending on the hardness of the material, they have a certain maximum stretching length. This limited length limits the stretching of the skin 252 of said piston.
• the common member 255 may slide with sliding means 256 over the piston rod 195. For the rest is the construction comparable with that of the piston 208,208' .
• Fig. 9C shows the longitudinal cross-section of the piston 258' .
• the contact area 253' .
• Fig. 10-12 deal with the management of the pressure within the container.
• Pressure management for the piston comprising an inflatable container with an elastically deformable wall is an important part of the piston-chamber construction. Pressure management has to do with maintaining the pressure in the container, in order to keep the sealing on the appropriate level. This means during each stroke where the volume of the container changes. And in the long term, when leakage from the container may reduce the pressure in the container, which may effect the sealing capability.
• a flow of fluid may be the solution. To and from the container when it changes volume during a stroke, and/or to the container as such (inflation).
• the change in the volume of the container may be balanced with a change in the volume of a first enclosed space, communicating with the container through e.g. a hole in the piston rod.
• the pressure may at the same time also be balanced, and this may be done by a spring force operated piston which may be positioned in the first enclosed space.
• the spring force may be originated by a spring or a pressurized enclosed space, e.g. a second enclosed space, which communicates with the first enclosed space by a pair of pistons. Any kind of force transfer may be arranged by each of the pistons, e.g.
• the tuning of the pressure in the chamber of the container during the entire or a part of the stroke may also be done by a communication of the chamber and the chamber of the container. This has already been described in WO00/65235 and WO00/70227.
• the container may be inflated through a valve in the piston and/or the handle of the piston rod.
• This valve may be a check valve or an inflation valve, e.g. a Schrader valve.
• the container may be inflated through a valve which communicates with the chamber. If an inflation valve is used, a Schrader valve is preferable because of its security to avoid leakages and its ability to allow to control all kinds of fluids.
• a valve actuator may be necessary, e.g. the one disclosed in WO99/26002 or in US 5,094,263.
• the valve actuator of WO99/26002 has the advantage that inflation may be enabled by a very low force - thus very practical in case of manual inflation.
• the valve closes automatically when equal pressure levels has been obtained.
• the flow of pressurized volume from the enclosed space to the container and vice versa may be substantial, it may be preferred to have a pressure/volume source with a bigger volume than the volume of the enclosed space and a pressure level which is equal, lower or higher than the pressure in the container. In the last mentioned case the volume of the pressure source may be reduced in comparison with a pressure source with an equal pressure level of that of the container.
• valves may have a springforce operated core pin, which may be is actuated.
• the actuators may open/close the valves of even contineously change the flow.
• An example is a analogeous construction used for inflating the container due to pressure drop by leakage (please see the next page).
• Other valve types and valve steering solutions are possible. This may also be a method of contiously maintaning the pressure level in the container at a predetermined level.
• valve may enable automatic inflation of the container, when the pressure in the container is lower than the pressure in the chamber.
• higher pressure in the chamber may be created temporarily by closing the outlet valve of the chamber near the second longitudinal position of the container in the chamber.
• This closing and opening may be done manually, e.g. by a pedal, which opens a channel which communicates with a space between the valve actuator (WO99/26002) and e.g. a Schrader valve.
• the valve actuator When open, the valve actuator may move, but lacks the force to depress the spring-force operated • core pin of the valve and hence the Schrader valve may not open - thus the chamber may be closed, and any high pressure may be build up for enabling inflation of the container.
• the actuator When the channel is closed, the actuator functions as disclosed in WO99/26002.
• the operator may check the pressure in the container by a pressure gauge, e.g. a manometer. Opening and closing of this outlet valve may also be done automatically. This may be done by all kinds of means, which initiate the closing of the outlet by a signal of any Jkind as a result of a measurement of pressure being lower than a predetermined value.
• the automatic inflation of the container to a certain pre-determined value may be done by a combination of a valve communicating with the chamber and e.g. a release valve of the container. It releases at a certain predetermined value of the pressure, e.g. to the space above the container or to the chamber.
• valve actuator of WO99/26002 may be open firstly when a pre-determined value of the pressure has been reached, e.g. by combining it with a spring.
• opening to the valve actuator is closed when the pressure reaches a value over the pre-determined one, by e.g. a spring force operated piston or cap.
• piston 292 of Fig. HE by combining the piston 292 of Fig. HE with means so that the piston opens the channel 297 when a certain pressure has been reached (not shown).
• Fig. 10A shows a piston-chamber system with a piston comprising a container 208,208' and a chamber 186 having a central axis 184 according to Fig. 6A-C.
• the inflation and pressure management described here may also be used for other pistons comprising a container.
• the container 208,208' may be inflated through a valve 241 in the handle 240 and/or a valve 242 the piston rod 195. If no handle is used, but e.g. a rotating axle, it could be hollow, communicating with e.g. a Schrader valve.
• the valve 241 may be an inflation valve, e.g. a Schrader valve, comprising a bushing 244 and a valve core 245.
• the valve in the piston rod 195 may be a check valve, having a flexable piston 126.
• the chamber between the check valve 242 and the chamber 209 of the container 208,208' was earlier described as the 'second' chamber 210.
• the manometer 250 enables control of the pressure inside the container - no further details are shown. It may also be possible to use this manometer to control the pressure in the chamber 186. It may also be possible that the chamber 209 of the container 208,208' has a release-valve
• the released fluid may be directed to the chamber 209 and/or to the space 251.
• Fig. 10B shows an alternative option for the inflation valve 241.
• a bushing 244 without a valve core 245 may be present, which enables connection to a pressure source.
• Fig. IOC shows details of the bearing 246 of the rod 247 of the check valve 126.
• the bearing 246 comprises longitudinal ducts 249 enabling passage of fluid around the rod 247.
• the spring 248 enables a pressure on the fluid in the second chamber 210.
• Fig. 10D shows details of the flexible piston 126 of the check valve 242.
• the spring 248 keeps the pressure on the piston 126.
• Fig. 10E shows the pressure source 701 which may have a pressure which exceeds the pressure level of the container.
• Inlet valve 702 with e.g. a valve actuator 703 (the configuration 709 shown is analogeous to the one of Fig. HE (292,297)), and outlet valve 704 with e.g. a valve actuator 705 (the configuration 711 shown is analogeous to the one of Fig. HE (292,297)).
• the space 710 is connected to the chamber 707, while the space 712 is connected to the chamber 708.
• the valves 702 and 704 may be mounted in the piston rod 706, which may be updivided in two chambers 707 and 708.
• Fig. 10F shows the construction of Fig.
• each a valve arrangement which may be steerable by external signals.
• the steering 715 may receive pressure signal 716 and 717, respectively from the inside of the piston at different longitudinal positions of the chamber.
• the steering 715 may send signals 718 and 719, respectively to the actuator 722 of the outlet valve arrangement 720 and to the actuator 723 of the inlet valve arrangenment 721.
• This valve and valve steering arrangement may be analogeously to the one shown in Fig.1 IF.
• Fig. IIA shows a piston-chamber system with a piston comprising a container 248,248' of which the central part is identical with container 208,208' and a chamber 186 having a central axis 184 according to Fig. 6A-C.
• the inflation and pressure management described here may also be used for other pistons comprising a container.
• the container 248,248' may be inflated through a valve communicating with the chamber 186.
• This valve may be a check valve 242 according to Fig. 10A,D or it may be an inflation valve, preferably a Schrader valve 260.
• the first enclosed space 210 is communicating with the chamber 209 in the container by a hole 201, while the first enclosed space 210 is communicating through a piston arrangement with a second enclosed space 243, which may be inflated through e.g. an inflation valve like a Schrader valve 241 which may positioned in the handle 240.
• the valve has a core pin 245. If no handle is used, but e.g. a rotating axle, it may be hollow and a Schrader valve may communicate with this channel (not drawn).
• the Schrader valve 260 has a valve actuator 261 according to WO99/26002.
• the foot 262 of the chamber 186 may have an outlet valve 263, e.g.
• a Schrader valve which may be equipped with another valve actuator 261 according to WO99/26002.
• the foot 262 may be equipped with a pedal 265 which can turn an angle ⁇ 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 (not drawn) for the chamber 186.
• the (schematically drawn) spring 276 keeps the pedal 265 in its initial position 277, where the outlet valve is kept open.
• the activated position 277' of the pedal 265 when the outlet valve is kept closed.
• the outlet channel 268 is provided in its initial position 277, where the outlet valve is kept open.
• Fig. 11B shows a detail of the communication by a pair of pistons 242,270 between the first enclosed space 210 and the second enclosed space 243.
• the piston rod 271 of the pair of pistons is guided by a bearing 246.
• the longitudinal ducts 249 in the bearing 246 enable the transport of fluid from the spaces between the bearing 246 and the pistons 242 and 270.
• the spring 248 may be present.
• Fig. llC shows an alternative wall 273 of the piston rod 272 of the piston type container ,
• the piston 274 is schematically drawn, and can adapt itself to the changing cross-sectional area's of the inside the piston rod 272.
• Fig. 11D shows piston 248' on which a housing 280 is build.
• the housing comprises a Schrader valve 260, with a core pin 245.
• the valve actuator 261 shown as depressing the core pin 261, while fluid may enter the valve 260 through channels 286, 287, 288 and 289.
• the piston ring 279 may seal the wall 285 of the inner cylinder 283.
• the inner cylinder 283 may be sealingly enclosed by sealings 281 and 284 between the housing 280 and the cylinder 282.
• Fig. HE shows the construction of the outlet valve 263 with a core pin 245, which is shown depressed by the valve actuator 261.
• Fluid may flow through channels 304, 305, 306 and 307 to the openened valve.
• the inner cylinder 302 is sealingly enclosed between the housing 301 and the cylinder 303 by sealings 281 and 284.
• a channel 297 having a central axis 296 is positioned through the wall of the inner cylinder 302, the wall of the cylinder 303 and the wall of the housing 301.
• At the outside of the housing 301 has the opening 308 of channel 297 a widening 309 which enables a piston 292 to seal in a closing position 292' by a top 294.
• the piston 292 may be moving in another channel 295 which may have the same central axis 296 as channel 297.
• the piston rod 267 may be connected to the pedal 265 (Fig. HA) or to other actuators (schematically shown in Fig. HE).
• Fig. 11F shows the piston 248' and the inflation arrangement 368 of Fig. 11D, besides the arrangement 369 to control the outlet valve of Fig. HE.
• the inflation arrangement 368 comprises now also the arrangement 370 to control the valve of Fig. HE. This may be done to enabling the closing of the valve, when the predetermined pressure has been reached, and opening it when the pressure is lower than the predetermined value.
• a signal 360 is handled in a converter 361 which gives a signal 362 to an actuator 363, which is actuating through actuating means 364 the piston 292.
• the arrangement 369 to control the closing and opening of the outlet valve 263 may be controlled by another actuator 363 through means 367 initiated by a signal 365 from the converter 361.
• a measurement in the chamber, giving a signal 371 to the converter 361 and/or 366 may automatically detect whether or not the actual pressure of the chamber is lower than the working pressure of the piston. This may be specifically practical when the pressure of the piston is lower than the pre-determined pressure.
• Fig. 11G shows schematically a cap 312, 312' with a spring 310 connected to the housing 311 of a valve actuator 315.
• the spring 310 may keep the opening 314 tigthly closed.
• the contact area 313 of the cap 312 with the cylinder 282 (fig. 11D).
• the spring 310 may determine the maximum value of the pressure to depress the valve core pin 245.
• a Schrader valve 260 may determine the maximum value of the pressure to depress the valve core pin 245.
• Fig. 12 shows en enlonged piston rod 320 in which a pair of pistons 321,322 are positioned at the end of a piston rod 323, which may move in a bearing 324.
• Fig. 13A,B,C show the combination of a pump with a pressurizing chamber with elastically deformable wall with different areas of the transversal cross sections and a piston with a fixed geometrical shape.
• a housing as e.g. cylinder with fixed geometrical sizes an inflatabel chamber is positioned which is inflatable by a fluid (a non-compressable and/or a compressable fluid). It is also possible that said housing may be avoided.
• the inflatable wall comprising e.g. a liner-fiber-cover composite or also added an impervious skin.
• the angle of the sealing surface of the piston is a bit bigger than the comparative angle of the wall of the chamber in relation to an axis parallel to the movement.
• This difference between said angles and the fact that the momentaneous deformations of the wall by the piston takes place a bit delayed provides a sealing edge, of which its distance to the central axis of the chamber during the movement between two piston and/or chamber positions may vary. This provides a cross-sectional area change during a stroke, and by that, a designable operation force.
• the cross-section of the piston in the direction of the movement may also be equal, or with a negative angle in relation to the angle of the wall of the chamber - in these cases the 'nose' of the piston may be rounded of.
• the wall of the chamber may be equiped with all the aheady shown loading regulating means the one showed on Fig. 12B, and if necessary with the shape regulating means.
• the velocity of the piston in the chamber may have an effect on the sealing.
• Fig. 13 A shows piston 230 at four positions of the piston in a chamber 231.
• a housing 234 with fixed geometrical sizes.
• a compressable fluid 232 and a non-compressable fluid 233 There may be a valve arrangement for inflation of the wall (not shown).
• the shape of the piston at the non-pressurized side is only an example to show the principle of the sealing edge. The distance between the sealing edge at the end and at the beginning of the stroke in the shown transversal cross-section is approximately 39%.
• the shape of the longitudinal cross-section may be diferent from the one shown
• Fig. 13B shows the piston after the beginning of a stroke.
• the distance from the sealing edge 235 and the central axis 236 is z x .
• the angle v is shown smaller than the angle ⁇ .
• the sealing edge 235 arranges that the angle v becomes as big as the angle ⁇ .
• Fig. 13C shows the piston during a stroke.
• the distance from the sealing edge 235 and the central axis 236 is ⁇ - this distance is smaller than z t .
• Fig. 13D shows the piston almost at the end of stroke.
• the distance from the sealing edge 235 and the central axis 236 is Z 3 - this distance is smaller than Zj.
• Fig. 14 shows a combination of a wall of the chamber and the piston which have 2-28 changeable geometrical shapes, which adapt to each other during the pump stroke, enabling a continuous sealing. It has its production size at the second longitudinal position of the chamber. Shown is the chamber of Fig.13 A now with only a non-compressable medium 237 and piston 450 at the beginning of a stroke, while the piston 450' is shown just before the end of a stroke. Also all other embodiments of the piston which may change dimensions may be used here too. The right choice of velocity of the piston and the viscosity of the medium 237 may have a positive effect on operations.
• the longitudinal cross-sectional shape of the chamber shown in Fig. 14 may also be different.
• Figs. 15 A-F show embodiments of the chamber with cross-sections of different sizes which have constant circumpherential sizes.
• the pistons according to claim 1 may also function well in these specific chambers, when the reinforcement of the skin allows parts of the wall of the container having different distances from the central axis of the chamber in a longitudinal cross-section of the chamber may also be used: e.g. the position of the reinforcement of e.g. Fig. 8D approximately parallell with the central axis of the chamber, and when the reinforcement is made of e.g. elastical threads (Figs. 6d,6E), or those shown in Figs.
• Pistons comprising non-elastically deformable containers or elastically deformable containers with a production size approximately the size of the circumpherencial length of the first longitudinal position of the chamber, having a reinforcement which allow contraction with high frictional forces may move in such chambers without jamming, and may jam in chambers where the cross-sections have different circumpherencial sizes. If the braid angle of the reinforcement of a container may become 54°44' the otherwise elastically deformable container becomes non-elastical deformable, that is to say flexible deformable, but it will not jam in these chambers, as it may be bent.
• the transversal cross-section of the pressurizing chamber and/or the piston can have any form, and this can be defined by at least one curve.
• the curve is closed and can approximately be defined by two unique modular parametrisation Fourier Series expansions, one for each co-ordinate function:
• Figs. 15A,15E show examples of said curves by using a set of different parameters in the following formulas. In these examples only two parameters have been used. If more coefficients are used, it is possible to find optimized curves which comply to other important demands as e.g. curved transitions of which the curves have a certain maximum radii and/or e.g. a maximum for the tension in the sealing portion which under given premisses may not exceed a certain maximum.
• Fig. 15F shows optimized convex curves and non-convex curves to be used for possible deformations of a bounded domain in a plane under the constraints that the length of the boundary curve is fixed, and its numerical curvature is minimized.
• the pistons shown in a longitudinal cross-section of the chamber have been drawn mainly for the case that the boundary curve of the transversal cross-section is circular. That is to say: in the case that the chamber has transversal cross-sections according to e.g. those non-circular of Figures 15A,15E,15F the shape of the longitudinal cross-section of the pistons may be different. All kinds of closed curves can be described with this formula, e.g. a C-curve (see PCT/DK97/00223, Fig. 1A).
• the inlet is positioned close to the end of the stroke due to the nature of the sealing portion of the piston means.
• Fig. 15A shows a series of transversal cross-sections of a chamber where the area i decreases in certain steps, while the circumference remains constant - these are defined by two unique modular parametrisation Fourier Series expansions, one for each co-ordinate function. At the top left is the cross-section which is the start cross-section of said series. The set of parameters used is shown at the bottom of the figure. This series show decreasing area's of the transversal cross-section. The numbers in bold in the figures show the decreasing cross-sectional area's of the different shapes, with the one in the corner left up as the starting area size.
• the area of the shape of the cross-section bottom, right is approximately 28 % of the one of the top, left.
• Fig. 15B shows a longitudinal cross-section of the chamber 162, of which the transversal cross-sectional area changes by remaining circumference along the central axis.
• the chamber has portions of different cross-sectional area's of its transversal cross- section of wall sections 155,156,157,158.
• Cross-section G-G has a circelround cross-section, while cross-section H-H 152 has approximately an area between 90-70% of the one of cross-section G-G.
• Fig. 15C shows transversal cross-section H-H 152 of Fig. 7G and in dotted lines as a comparison cross-section G-G 150.
• Cross-section H-H has approximately an area between 90- 70% of that of cross-section G-G.
• the transition 151 which is made smooth. Also shown is the smallest part of the chamber, which has approximately 50% of the cross-sectional area of cross- section G-G.
• Fig. 15D shows a transversal cross-section I-I of Fig. 7G and in dotted lines as a comparison cross-section G-G.
• the cross-section I-I has approximately an area of 70% of that of cross-section G-G.
• the transition 153 is made smooth.
• Fig. 15E shows a series of transversal cross-sections of a chamber where the area decreases in certain steps, while the circumference remains constant - these are defined by two unique modular parametrisation Fourier Series expansions, one for each co-ordinate function. At the top left is the cross-section which is the start cross-section of said series. The set of parameters used is shown at the bottom of the figure.
• the size of the cross-sectional area bottom right is approximately 49% of the starting area size left, top.
• Fig. 15F shows a convex curve optimized for a certain fixed length of the boundary curve, and a smallest possible curvature.
• the general formula for the smallest radius of curvature, corresponding to the largest curvature of the figure shown in Fig. 7L is:
• the length specified by y is determined by:
• A] decreased value of the starting domain area A 0
• Fig. 16 shows a combination where the piston comprising an elastically deformable container 372 which is moving in a chamber 375 within a cylinder wall 374 and a taper wall 373 e.g. shown her in the centre around the central axis 370.
• the piston is hanged up in at least one piston rod 371.
• the container 372,372' is shown at the second longitudinal position of said chamber (372') and at the first longitudinal position (372).
• Fig. 17A shows a convex chamber 400 witin a wall 401. "s" means stroke.
• Fig. 17B shows the Force-Stroke diagram in the direction shown in Fig. 17A. This curve shows the optimized change of the force when an operator is pumping in strokes where the intake of fluid lies approximately at the first longitudinal position of the chamber and the outlet is approx. at the second longitudinal position of the chamber. The curve tangents the maximum operating force approximately at the end of the pumping stroke.
• Fig. 18A shows an example of a Movable Power Unit 500, shown movable by parachute 501, and by wheels 502.
• Fig. 18B shows the Movable Power Unit 500, with a power unit comprising a set of solar cells 503 on top and a motor 504. Moreover a water pump 505, and a compressor 506. The steering unit 507.

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• Containers And Packaging Bodies Having A Special Means To Remove Contents (AREA)
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• 2003
  • 2003-10-02 BR BR0314510-7A patent/BR0314510A/pt not_active IP Right Cessation
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