EP2917611A1

EP2917611A1 - Piston-chamber combination - vanderblom motor

Info

Publication number: EP2917611A1
Application number: EP12758741.8A
Authority: EP
Inventors: Nicolaas Van Der Blom
Original assignee: NVB Composites International UK Ltd
Current assignee: NVB COMPOSITES INTERNATIONAL UK Ltd
Priority date: 2011-07-01
Filing date: 2012-07-02
Publication date: 2015-09-16
Also published as: WO2013026508A1; AU2012299891A1; JP2014527601A; IN2014CN00659A; AP2014007764A0; CA2878083A1; JP2022105333A; AU2012299891A8; BR112014000028A2; KR20140094498A; MX2014000225A; WO2013026508A4; CN103782070A; JP2024045410A; JP2020029864A; JP2018076864A; TW201321596A

Abstract

A piston - chamber combination comprising a chamber (186) which is bounded by an inner chamber wall (185) and comprising a piston inside said chamber to be engagingly movable relative to said chamber wall at least between a first longitudinal position (208) and a second longitudinal position (208 ') of the chamber, said chamber having cross - sections of different cross - sectional areas and different circumferential lengths at the first and second longitudinal positions, and at least substantially continuously different cross - sectional areas, said piston comprising a container which is elastically deformable. The piston is produced to have a production - size of the container in the stress -free and undeformed state thereof. This is accomplished by the combination comprising means for introducing fluid from a position outside (210) said container into said container, thereby enabling pressurization of said container, and thereby expanding said container, a smooth surface of the wall of the actuator piston, at least on and continuously until nearby its contact area with the wall of the chamber, thereby displacing said container from a second and to a first longitudinal position of the chamber.

Description

19627 - Piston - Chamber Combination Vanderblom Motor 01-07-2012

19627 TECHNICAL FIELD

A piston-chamber combination comprising a chamber which is bounded by an inner chamber wall and comprising an piston inside said chamber wall to be engagingly movable relative to said chamber wall at least between first and second longitudinal positions of said chamber, said chamber having cross-sections of different cross-sectional areas and differing 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 actuator piston comprising a container having an elastically deformable container wall for engagingly contact with the chamber wall, said container being elastically deformable to provide for different cross-sectional areas and differing circumferential lengths of the piston for adaptation to said different cross-sectional areas and different circumferential 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 the actuator piston is produced to have a production-size of the container in the stress-free and undeformed state thereof in which the circumferential length of the actuator piston is approximately equivalent to the circumferential length of said chamber at said second longitudinal position.

19627 BACKGROUND OF THE INVENTION

This invention deals with solutions for alternatively and efficiently functioning actuators, in relation to existing actuators, and with the important goal of such actuators for fighting climate change, in motors, and specifically car motors. Additionally deals this invention with solutions for an efficient shock absorber, and a pump. This invention deals specifically with solutions for the problem of obtaining a motor, which does not use combustible techniques of oil derivatives like petrol, diesel, and which can compete with current motors based on said combustible technics. And additionally to comply with the demand for reducing C0₂- emission, so as to compete as well with combustible motors based on H₂, or even air, as it does not need new distribution networks for providing the energy source for the motor.

The combustible motor based on oil derivatives is after today's technical standards only an optimized version of a concept which is approximately one century old. This means that it does not comply anymore to today's standards of living: a waist of valuable and limited available oil, and a source of pollution, such as emission of among others toxic gasses like CO, and gasses like C0₂ which is an important cause of the climate change. Additionally combustible motors tend to be heavy, so that the Transport Weight Ratio (= weight of one person in relation to the weight of what is being transported in total) may be approx. 12 (small passenger car) - 33 (limousine, 4 wheel drive) for a passenger car.

The new combustible motors based on ¾, or even air are lacking the distribution network for deliverance of the energy sources for said motors, such as petrol stations today for the delivery of petrol, diesel and NLG gas. Even the current motor functioning on air needs 'filling' stations for providing the necessary high compressed air in large and heavy cylinders - the lack of such a distribution network was the reason why said motor on air is constructed in such a way that is also can function on combustible means e.g. petrol or diesel - thus back to the Otto Motor again, which ought to be avoided.

The setting up of new networks of providers for these last mentioned new to be used combustible materials needs very high financial investments, and that gives difficulties due to the Catch 22 situation: without a proper fine masked network will these motors not be distributed, because nobody will buy such motor, due to lack of availability, and nobody wants to invest in the network, before there is evidence that there is a market. For a quick introduction and widespread distribution of a non-polluting motor, it is necessary that this motor is independent of networks for providing the energy source. A current development of a home filling station for H₂ seems an interesting but quite so tricky thought, because this gas is a very dangerous gas, and should only be handled by instructed personnel. 19627 OBJECT OF THE INVENTION

The object is to provide combinations of a piston and a chamber to be used in pumps, actuators, shock absorbers and the use of said actuators in among others a motor.

19627 SUMMARY OF THE INVENTION

In the first aspect, the invention relates to a combination of a piston and a chamber, wherein: the combination comprises means for introducing fluid from a position

outside said piston said container, thereby enabling pressurization of said container, and thereby expanding said container and displacing said container between second and first longitudinal positions of the chamber.

A classic actuator piston is positioned in a straight cylinder, and said piston is comprising a piston rod. It is moving as a consequence of a pressure difference between both sides of said piston - the last mentioned may be a piston, which is made of a non-elastic material and comprising at least a sealing ring, sealing the piston to the cylinder wall, in which the piston is relatively moving to said cylinder. A piston rod may be guided by a bearing on one or both sides of the cylinder. The piston rod outside the cylinder may be pushing or pulling an external device. It may also be engaging a crank shaft, so that a rotation occurs of the crank shaft axel, which may result in motion of e.g. a vehicle, comprising said actuator and crank shaft.

The actuator piston, when positioned in a straight cylinder may also be an inflatable piston, e.g. a container type piston according to claim 5 and claims 28 and 34 of EP 1 179 140 Bl. If said inflatable piston has been pressurized inside, its, preferably reinforced, wall may engage or seal, respectively to the wall of the cylinder, and may act regarding its motion in said cylinder, as the above mentioned classic piston in said straight cylinder. For enabling the motion, a valve on both sides of the piston, e.g. in the wall of the chamber, may be necessary, and a fluid in the cylinder on both sides of said piston with a certain pressure difference, preferably controlled by control means. Changing the size of the pressure inside the last mentioned container wall may only have an influence on the ability to engage or seal of said piston wall to the wall of the chamber. Still, through the friction between the wall of the container, and the wall of the chamber, said internal pressure may have influence on the- speed of the motion of the piston.

An actuator according to the invention is a piston chamber combination which has an inflatable piston. Inside the piston may preferably be a fluid and/or a foam under a certain pressure, the piston of which its wall comprising material(s) and preferably reinforcement(s) may allow it to change shape and/or size, and the piston may be moving in the chamber or vice versa preferably without the need for a fluid in the chamber and/or without a pressure difference of said fluid or foam on both sides of the piston in the chamber - a fluid in the chamber may of course still be present as e.g. air at atmospheric pressure, e.g. for control purposes.

A further necessary parameter may be that the wall of the chamber is not parallel to the centre axis of said chamber, while the angle of said chamber wall in the direction of the intended motion of the piston has a positive value, so that the piston can expand in said direction. Expansion may preferably be done from a second longitudinal position of the piston, where the piston has its smallest circumferential size: its stressfree production size, to a first longitudinal position of said piston, where the piston has its biggest circumferential size - please see EP 1 384 004 Bl .

The motion of the piston may be initiated by the forces towards the inner chamber wall of said container type piston which arise, when the container is expanding. Thus said motion may be initiated by reaction forces from the wall of the chamber to the wall of the container. These forces are a reaction on the expansion of the wall of said container, and said expansion may be a consequence of increasing the volume and/or pressure of the fluid in the piston, as a result of the introduction of more fluid through an enclosed space from a position outside said piston to said container.

In a working prototype of a piston according to Figs. 7A-C (WO 2004/031583) with a reinforcement of Fig, 8D (WO 2004/031583) is the piston roc ting from a second longitudinal position to a first longitudinal position, and if unloaded, with a fluctuating speed in a chamber with a so-called constant maximum working force shape (WO2008/025391 - Fig.6B), already at a few Bars overpressure inside the piston in relation to the atmospheric pressure, which was present at both sides of the piston in the chamber, and with a fluctuating positive angle of the inner chamber wall with the centre axis of said chamber in the direction from a second to a first longitudinal position. Said experienced fluctuation of the speed of the piston is explained below.

The contact between the wall of the container and the wall of the chamber may be engagingly or sealingly. It depends more or less on the load on the piston rod, as said prototype reveals. With no load on the actuator, the contact may be engagingly, and not sealingly. With a load on the actuator, the driving forces on the container are bigger than in the case without a load on said actuator, which is why there may be enough force on the chamber wall from the wall of the container, so that the contact between said walls is sealingly. It may also be that during a move of the piston the contact with the wall of the chamber may be sequentially engagingly and sealingly.

The reasoning why the piston is moving may be as follows. If the longitudinal component of the reaction force from the wall of the chamber to the wall of the container, which is directed to a first longitudinal piston position, is bigger than the longitudinal component of the friction force between the wall of the chamber and the wall of the piston, which is directed to a second longitudinal piston position, the total resulting force will be directed toward a first longitudinal piston position, and consequently the piston will move from second to first longitudinal positions. As preferably the end of the container closest to a second longitudinal piston position is fastened to the piston rod by a cab (192), the piston rod will move as well. A self-propelling actuator has been born, which may be the alternative for a piston which is moving by a pressure difference outside said piston, inside the chamber. Preferably is the other end of the container slidingly movable over the piston rod by means of a cab (191), which means to that the expansion of said container brings said cabs (191) and (192) closer to each other, by the movement of cab (1 1) toward the cab (192) over the piston rod. This is due to the chosen reinforcement of the wall of the container, which is preferably a one layer of reinforcement strings directed from cab (191) to cab (192), which lies in a plane which is parallel to the centre axis of said chamber (e.g. WO2004/031583, Fig.8D), and optionally with a slight angle with the centre axis of the chamber and/or at least two layers of reinforcements crossing each other with a very small angle.

Due to the positive slope of the wall relative to the centre axis of said chamber in the direction of first longitudinal piston positions, and the fact that the contact surface of the piston and the wall of the chamber is positioned in the longitudinal direction preferably under the middle point of the elastically deformable wall of the piston, optionally approximately just under said middle point of the elastically deformable wall of said piston, said movement will result in an expansion of the wall of the container. Thus the original contact area between said walls will become larger, and an increased friction force results. Said motion may slow down, as the total resulting force toward first piston positions decreases.

Approximately at the same time that the wall of the container between said increased contact area and said movable cap is expanding, said motion will result in that the cap (191), the movable end of the piston, is coming closer to the cap (192) which is fastened to the piston rod. This means that due to the still present overpressure inside said container (the volume of the enclosed space may need during the motion from second to first longitudinal piston positions to be constant), the reinforcement in the wall of said container, said wall is expanding as well, more round nearest a second longitadinal position. This means that the wall of the container is rolling over the wall of the chamber, so that said contact area moves toward first longitudinal positions, thereby increasing the component of the reaction force of the wall of the chamber to the wall of said container. The component of the resulting force toward first longitudinal piston positions will increase and will become rapidly bigger than the friction component, so that the part of the container closest to the second longitudinal piston position is moving with increasing speed toward first longitudinal piston positions, thereby taking the non-movable cap (192) with it, thus also the piston rod - the piston is moving from a second to a first longitudinal piston position.

The overpressure is measured in relation to the atmospheric pressure, which is why when the piston may be positioned inside a closed chamber, the last mentioned may need on both sides of the piston to be able to communicate with its surroundings of the combination, which may preferably be under atmospheric pressure.

Instead of the enclosed chamber space may the fluid in the chamber communicate with an enclosed chamber space, so that fluid in the chamber is not prohibiting said movement of said piston. This is a concept which may be used in a shock absorber.

Whether or not an enclosed chamber space or a channel to the atmospheric surroundings may be necessary depends on the sealing ability of the piston to the chamber wall. A leakage of the piston to the wall may also due, and may be present, as a 100% sealing of the piston to the chamber wall may not be necessary (engaging). Thus, a channel which connects the spaces of the chamber on each side of said container, may be interconnected by a channel, which said piston is comprising.

Said piston may comprising an enclosed space, e.g. a hollow piston rod. The inside of said piston may be communicating with said enclosed space. The volume of said enclosed space may be constant or variable, and adjustable. Said enclosed space may be communicating with a pressure source.

In the second aspect, the invention relates to a combination of a piston and a chamber, wherein: A piston-chamber combination further comprising means for removing fluid from said container through said enclosed space to a position outside the piston, thereby enabling contraction of said container.

The movement during the return part of the stroke of said piston from its first longitudinal position to a second longitudinal position may be done by at least three possible ways.

The traditional way, where the piston is sealingly engaging the wall of the chamber. Said movement however may cost energy, because the surplus of the fluid inside the container type piston, which is shrinking and by that is reducing its internal volume, may be transported towards said enclosed space, of which its internal pressure may increase. In order to save energy, the piston may engage, but not seal to the wall of the chamber - this will reduce the friction force between said piston and said chamber wall. The last way may be done by reducing the internal pressure of the container during said part of the stroke, by sucking out the fluid from the container That may be accomplished by controlling means, controlling the pressure in said enclosed space. In the third aspect, the invention relates to a combination of a piston and a chamber, wherein: the piston is movable relative to said chamber wall at least from first to second longitudinal positions of said chamber. It may be possible to move the piston from first to second longitudinal positions, without engaging the wall of the chamber. This may be done by reducing the pressure inside the piston to a minimum level, e.g. that the wall of the piston is stressfree and its cixcumference is that of its production size at a pressure when it was produced (e.g. the atmospheric pressure), so that the piston can arrive at a second longitudinal position without jamming.

In the fourth and fifth aspects, the invention relates to a combination of a piston and a chamber, wherein the piston is comprising a piston rod, which is comprising said enclosed space. the piston is comprising engaging means outside said chamber. The suspension of the piston rod may be special, e.g. according to those bearing types shown in WO2008/025391, in order to guide the piston during said part of the stroke, without the guidance of the piston itself, if the piston would not engage the wall of the chamber.

The piston rod may be extending from the piston in one longitudinal direction, and guided by a bearing at an end of the chamber. That means that the piston rod may comprising the enclosed space, and also comprising an engaging means, e.g. positioned outside the chamber. The engaging means may be pushing or pulling when the piston is moving from second to first longitudinal positions. The other way around would the engaging means not be able to push nor to pull. A force outside the piston may be driving the piston from first to second longitudinal positions. When the piston may not be sealingly moving from first to second longitudinal positions, a force on the piston rod may be driving the piston, when the piston is comprising the piston rod. This may be accomplished by said engaging means.

It may however also be possible that the piston is comprising a piston rod which extends in two longitudinal directions, and one piston rod may normally be a continuation of the other. One or both piston rods may comprising engaging means, e.g. positioned outside the chamber. When both piston rod ends may extend outside the chamber, one bearing of the piston rod may be fastened rigidly to the chamber, while the other may be floating in relation to the chamber. The engaging means may be pulling and pushing at the same time, when the piston is moving from second to first longitudinal positions. The other way around - the return stroke - would the engaging means not be able to push nor to pull. A force outside the piston may be driving the piston from first to second longitudinal positions. When the piston may not be sealingly moving relative to the chamber from first to second longitudinal positions, a force on the piston rod may be driving the piston, when the piston is comprising the piston rod. This may be accomplished by said engaging means.

In the sixfli and seventh aspect, the invention relates to a combination of a piston and a chamber, of which the piston rod is connected to a crankshaft, wherein: a crank is adapted to translate the motion of the piston between

second and first longitudinal positions of the chamber into a rotation of said crank. the crank is translating its rotation into a movement of the piston from first to second longitudinal positions of the piston.

The engaging means may be a crankshaft, which is connected to the piston by said piston rod. In order to be able to at least initiate the motion of the piston from first to second longitudinal positions of the chamber, the crankshaft should turn before said motion commences by said piston, so that the impuls of the contra weights of said crankshaft generated by the motion of the piston from second to first longitudinal positions can be transferred to the piston.

Another option is that the motion of the piston between first and second longitudinal positions may be done by the motion of the crankshaft, initiated by e.g. another piston-chamber combination, of which the piston is simultaneously moving from second to first positions of its chamber (at least two cylinder, working together on the same crankshaft).

The initial motion of the piston may done be e.g. an electric motor, which initiates and shortly maintains the rotation of the crankshaft - a kind of starter motor - until the crankshaft is turning by a piston chamber combination.

In the seventh and eigth aspect, the invention relates to a combination of a piston and a chamber, of which the piston rod is connected to a crankshaft, wherein: the crankshaft is comprising a second enclosed space. the second enclosed space is communicating with a power source. The crankshaft may be hollow and comprising a second enclosed space. This means that the crankshaft axel and its contraweights are hollow, in such a way, that these together form a channel from a container type piston toward the end of the crankshaft axel. With an O-ring sealing may this channel be communicating with a pressure source

It may also be positioned in the crankshaft inclusively the axis bearing of said crankshaft, so that it may be communicate with an external power source.

In a nineth aspect, the invention relates to a combination of a piston and a chamber, wherein:

- said second enclosed space is communicating with the first enclosed space in the piston rod during a period of the time when the piston is moving from first to second longitudinal positions of the chamber.

During the part of the stroke from first to second longitudinal positions, the piston may be depressurized to a certain pressure level at which the piston was produced, and this may be done by connecting the first enclosed space in the piston to the second enclosed space in the crankshaft the necessary period of time during the time when the piston is moving from first to second longitudinal positions. The pressure level under which the piston was produced may not be atmospheric pressure, but may be any pressure level. The higher the pressure level is, the less energy may be lost, when the first and second enclosed space are connecting to each other.

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

said crankshaft is comprising a third enclosed space, which is communicating with the first enclosed space of the piston rod during a period of the time when the piston is moving from second to first longitudinal positions of the chamber.

This third enclosed space has the function to pressurize the piston again, when its movement changes direction from moving toward a final second longitudinal position of the chamber towards a first longitudinal position of the chamber. The pressurization is done by connecting the third enclosed space, which has overpressure in relation to the first enclosed space, to the first enclosed space. Pressurization may be done as quickly as possible after the motion of the piston has changed direction.

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

said third enclosed space is communcating said second enclosed space during a period of the time when the piston is moving from second to first longitudinal positions of the chamber.

A shock absorber comprising:

a combination according to all earlier mentioned aspects,

means for engaging the piston from a position outside the chamber, wherein the engaging means have an outer position where the piston is at the first longitudinal position of the chamber, and an inner position where the piston is at the second longitudinal position.

A shock absorber may further comprising an enclosed space, which may communicating with the container. The enclosed space may have has a variable volume, or a constant volume. The volume may be adjustable.

A shock absorber may comprise the container and the enclosed space which may forming an at least substantially sealed cavity comprising a fluid, the fluid may be compressed when the piston moves from the first to the second longitudinal positions of the chamber.

A pump for pumping a fluid, the pump may comprising means for engaging a second piston in a second chamber from a position outside the chamber, a fluid entrance connected to the second chamber and comprising a valve means, and a fluid exit connected to the second chamber.

A pump wherein the engaging means may have an outer position where the piston may be at the first longitudinal position of the chamber, and an inner position where the piston may be at the second longitudinal position of the chamber. A pump, wherein the engaging means may have an outer position where the piston may be at the second longitudinal position of the chamber, and an inner position where the piston may be at the first longitudinal position of the chamber. The technology of the piston-chamber combination may be used in a motor, specifically in a car motor - specifically the self-propelling actuator.

The piston may also move relatively with the tapered wall, within a chamber, which may be cylindrical, or conical (not shown).

The chamber in which the ( actuator) piston is positioned, may be of the type wherein said chamber may be comprising internal convex shaped walls of longitudinal cross-sectioned sections near a first longitudinal position, said section may be updivided from each other by a common border, a distance between two following common borders defines the height of the walls of said longitudinal cross- sectional sections, said heights are decreasing by an increasing internal overpressure rate of said piston, or in the direction from first to second longitudinal position the transversal length of the cross- sectional common borders may be determined by the maximum work force, which may be chosen constant for said common borders. Additionally may said chamber comprising a wall of a cross-sectional border which is parallel to the centre axis of said chamber.

And, said piston-chamber combination may comprise a transition between said convex shaped walls and said parallel wall when said transition may be comprising at least a concave shaped wall, which may be positioned near a second longitudinal position. And said piston-chamber combination may comprise a concave shaped wall, which may be positioned at least on one side to a convex shaped wall.

19627 SUMMARY OF THE INVENTION - feasibility study

The feasibility study for a 'green' motor is as follows - please review Fig. 10B and Fig. 1 IB which gives a good helicopter view on the issue. This is a system, where the output of the motor is being generated by a new propulsion system, where an inflatable actuator piston in a chamber with continuously differing cross-sectional area's, is moving by means of internal pressure from a smallest cross-sectional area to a bigger one, thereby decreasing internal pressure, while during the return stroke the fluid of said actuator piston is further depressurized, wherein said fluid is being repressurized by a cascade pumping system using the energy efficient piston-chamber combination according to WO2000/070227, of which at least one step is being energized by an external green power source, e.g. the sun, or preferably any other sustainable power source, or optionally a non-sustainable power source. Still more efficient and reliable solutions can be seen in Figs. 1 1G and 13F. That system is complying to the earlier stated specifications.

TRANSLATIONAL POWER SOURCE for a 'green' motor based on the principle of Fig. 11 A

The overall system solution regarding this invention is, that said 'green' motor as such may be based on comparable construction elements as currently used in combustible engines, but that the new construction elements need to function much more efficiently than those of current combustible motors, and so much more, that the energy used, may be obtained from preferably a 'green' energy source, e.g. like the sun, combustion of H₂ generated preferably when the motor is running by e.g. electrolyses, or optionally by a H₂ refillable storage tank + fuel cell, and/or from a pressure storage vessel, containing a pressurized fluid, preferably of low pressure (e.g. approx. 10 Bar), optionally of high pressure (e.g. <300 Bar) filled once and for all while the motor is produced and preferably repressurized during operation of said motor, optionally refilled when the motor is out of operation, and/or a battery, charged when the motor is produced, and preferably continuously recharged when the motor is running, and/or optionally recharged when the motor is not running, and from the system itself, preferably because the energy needed may be less than the available total energy which the system may perform for the task of generating motion, optionally from another power source WO2000/070227 discloses a piston-chamber combination technology which can save a substantial amount of energy e.g. up to 65% energy for a pump at 8 Bar (the current working pressure of car motors) - e.g. 10 Bar in a tube with an 17 mm (from ø 60mm at first longitudinal positions), at second longitudinal piston positions, if the smallest cross-sectional area of a chamber is positioned there where the highest pressure occurs: at a second longitudinal position. The other way around, by using said technology in an actuator instead of a pump, is of even efficiency. WO2004/031583 discloses an expandable piston type (e.g. ellipsoide→ sphere: small sphere <→ big sphere) which is not jamming in said chamber, when the non-stressed production size of a piston has a circumference, which is approximately the size of the circumference of that part of said chamber which has the smallest cross- sectional area: this may be at a second longitudinal position. This piston type shows special characteristics, used as an actuator piston in said chamber, and these characteristisc are claimed in this invention: the actuator is self-propelling, if said piston is pressurized through its enclosed space from a pressure source outside said chamber, at said second longitudinal position, and when there is no pressure difference between both sides of said piston in said chamber, while there is an angle not being zero between the wall of the chamber and the centre axis of said chamber - in a working prototype is the actuator piston expanding and rocketing with 260 N to first longimdinal piston positions, where the cross-sectional area is largest, in a chamber which has been designed having a constant maximum working force of 260 N (WO2008/025391, WO2009/083274). This phenomenon may be used in this 'green' motor, thereby exchanging motion based on energy derived from combustible technics, however still using a crankshaft. The energy used due to the expansion may be approximately 5 Bars (e.g. from 10 Bar to 5 Bar overpressure, due to an increase of the piston's volume), e.g. from ellipsoide→ sphere by a constant volume of the enclosed space (WO2009/083274). This pressure drop has to be re-gained in the system, because in the return stroke, the actuator piston needs to become unstressed at a second longitudinal piston position, where it has its production size, thus with e.g. 0 bar internal overpressure. The 5 Bar overpressure at first longitudinal piston positions can be re-used, when the piston's enclosed space is connected to another enclosed space, which may be positioned e.g. within the crankshaft, and which is through an e.g. two-stepped pumping process, increasing the pressure from 5 Bar to 10 Bars again. This may be done efficiently by using another aspect of the piston-chamber combination technology which is disclosed in WO2000/070227, so that in the repressurization process also a 65% energy may be saved: e.g. by using a piston based on e.g. claim 1 of EP1179140B1 or on Figs.5A - 5H of WO2000/065235, of which further developments are additionally claimed in this invention. From these 65% energy reduction can still additional energy be saved, by connecting the crankshaft of said pump to the main crankshaft of said actuator piston: say, said additional saving may be assumed to be 35%. Thus total savings are: 76,7 % (65 + 1/3 x 35%). Thus 23,3 % of the energy should be gained from another pump, e.g. identical with the last mentioned, but which now is getting its energy from e.g. an electric motor which receives its electricity^" from said battery charged optionally by a solar cell (which should not be bigger than a roof of a common car, or a solar cells, incorporated in the paint of a car), or optionally by a fuel cell, or preferably by an alternator, which may gets its rotation from an axle of the system of the motor itself or from an axle of a small H₂ combustible engine.

The energy necessary for letting that pump function is 35% of the 23,3 % which is 8,2 %

Neither heat may be generated by said motor, nor noise, while the weight of this motor may be substantially (e.g. 60%) lower than that of current combustible motors, while almost all additional controlling devices which a combustible motor needs, such as contiolling water temperature for cooling purposes, oil temperature and the exhaust system, may be unnecessary, as well as a petrol tank - with an aluminum an/or plastic body, may the future car be half of the weight of current cars - e.g. a VW Golf Mark II weights 836 kg, while designed and produced according to this invention may it weight approx. 425 kgs: with only the driver present is the TWR: 6,3 !

A problem remaining may be driving during a long time in the dark of the night, when solely a solar cell may be used for recharging said battery. However, the light of lamps of lamp posts in the streets of a town may give enough light for the solar energy cell.

And, a gearbox may be necessary, because the rpm's of such a 'green' motor may be lower than that of current combustible motors.

19627 ( amended ) added matter to the description - feasibility study in 19618

The feasibility study until now did not incorporate quantitatively the lack of heat generated by a motor of this invention, in comparison with Otto Motor types. When heat loss may be incorporated, than the motor types of this invention are still more interesting and convincing. Heat losses may give a current Otto Motor an efficiency of 25%. When it may be assumed in the first instance that said motor types of this invention do not generate heat at all (isothermal), than it may be possible to reduce the energy used to pressurize the fluid from 5 Bar to say 10 Bar (10 Bar was already present in the pressure storage vessel, when the motor was produced) by approx. 65%. The total efficiency of a motor type according to this invention may then come under 10%, namely 8,75%, by the self-propelling actuator piston, and this is up to now may be unprecedented (David JC Mackay, Sustainable Energy - without the hot air - 2009). When the pumps for regenerating pressure, shown in this invention, again are using the piston-chamber combination types according this invention, than another 65% of energy may be saved. Thus this may result in a total energy use of 8,75% x 0,875 = 7,6%, if we would disregard that heat is being generated by the pump. However, when a part of the energy used for pumping may come from another energy source (than from the total motor power), such as a battery, charged by e.g. solar energy (photovoltaic) and/or a fuel cell (e.g. a H₂), from a flywheel or from regenerative braking devices coupled to a generator, than the total used energy still may end under 10%.

Earlier has already been concluded that the configuration of a motor type according to Fig. 11G, 15C or 15D and Fig.l3F,G and Fig.l4D may be the most efficient (simple construction, almost isothermal thermodynamics), and may additionally be the most reliable (no leaks), and of which the configuration of Fig. 13F,G and Fig.HD is without the use of a crank generating rotation, will the configuration of Fig. 13F be used in a quantitative assessment of a car motor.

We use a current VW Golf Mark II model RF, 1600cc, weight 836kg, with a 53 kW / 71 pk gasoline motor, comprising 4 cylinders of each ø 81mm, and a pressure of 9 Bar, and a stroke of 77 mm as a benchmark for the invention. This gives a max. force of 1159 N per cylinder, which is approx. 1 16 kg per cylinder. A weight reduction of approx. 50% may be assumed, if all the combustion parts would be taken out of the car body, and aluminium would be used instead of steel for said body. Thus necessary may be 58 kg per cylinder to drive an aluminium body, up to 4 passengers and luggage. The chamber of the pump shown in WO2008/025391 has a max. working force of 260N (26 kg), over approximately the whole stroke of 400mm from 2 - 10 Bar, and with a diameter of ø 58mm - 0l7mm, respectively. Using an inflatable ellipsoi'de shaped piston in this chamber, the actuator is functioning very well in practise. Thus, two of these chambers, now used as part of an actuator could be equivalent with one cylinder of the gasoline motor of said VW Golf Mark II, now made of aluminium, and all parts related to combustion taken out.

In the motor according to this invention, will the pressure in the enclosed space of an actuator piston be changed from x Bar (stroke: 2^nd→ 1^st longitudinal positions) to approx. 0 bar (stroke: 1st→ 2^nd longitudinal positions). The value of "x" may be chosen as small as possible, in order to limit the energy use. Because using said special chamber type, the size of the working force is independent of the pressure value, it may be possible to limit the pressure with using a pressure window to 3,5 Bar at the highest level to approx. 0,5 Bar at the lowest level.

Said starting points may be taken over to the configuration of the pressure in the sphere shaped piston, positioned in a rotating chamber of Fig. 13F - however, the chamber may now be still more simply shaped as the one shown in Fig. 13F, as 3½ Bar uses only a part (216,2mm of the 400mm) of the stroke in said specific chamber - the Force per actuator piston is max. 260N.

The change of the volume of said sphere may be quite big: from

V₂= 4/3 x 3,14 x 12,55³ (025.1mm; P₂=0,35 N/mm²)= 8280 mm³ to Vi= 4/3 x 3,14 x 23,45³ (ø 46.9mm; Pi=0,05 N/mm²) = 54015 mm³ - which is a AV of 6,5 and a ΔΡ = 7. The angle of the wall relative to the centre axis of said chamber is: L₁=302,78 - 86,57= 216,21, Δτ= 10,9: angle= 2,9°- this angle is good.

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

Wisothermai = -PiV₁ln(P₂ Pi)= 0,35 x 54015 x In 7= 0,35 x 54015 x 2,302585 x log 7 = 36788 Nrnm/channel/piston/revolution = 36,8 J/channel/piston/revolution, if there would only be one actuator piston per channel. Said motor according to this invention is not as quick as said gasoline motor (900 rev/m), regarding the number of strokes/minute - this is due to the assumed slower expanding and contracting of the actuator piston, which is made of reinforced rubber. Let us assume the number of revolutions/minute is 60, thus 1 per second (15x slower than said combustible motor). The W= 36,8 J/channel/piston/s. There are 2 x 4 'comparable' chambers (cylinders) - the power is than 294,3 J/s/piston, which is 0,295 kW/piston. When using 5 pistons, one in each of the 5 sub- chambers of each of said 360° channels (Fig. 13F), than may the generated power be: 5 x 0,295 kW = l,47 kW.

Check of the assumption 1 revolution per second: a combustible gasoline motor amounting 53 kW, of which it was stated earlier in this study, that it may save 92,4%: 7,6% may only be used: 4,03 kW.

That may firstly complying to the above mentioned calculation, if the number of revolutions per second may approx. be (rounded off): 3 revolutions/sec.

Thus, a motor comprising 2x4 'comparable' chambers, each comprising 5 pistons in 5 sub-chamber, rotating at 3 revolutions per second (= 180 rev/min.), resulting in a power of approx. 3 x 1,47 =

4,4 kW - this may be enough to drive a VW Golf Mark II with an aluminium body.

The literature (David JC Mackay, Sustainable Energy - without the hot air - p.127, Fig.

20.20/20.21) reveals a small electric car using approx. 4,8 kW power to run, and which is coming from 8x 6V batteries - that car could run 77 km on one batteries' charge, and charging time is several hours. If the energy is coming from batteries, which cannot be charged during the drive of said car, this may be an option, but not a preferred embodiment.

How much energy is necessary to get the actuator pistons pressurized and depressurized, and, can that be done while the car is driving?

It is necessary to get the pressure change in said actuator pistons of said motor energized. We use the principle shown in Fig. 1 IF and Fig. 13F.

The energy may come from the kinetic energy from said rotating chambers, where e.g. the piston of a classic piston-chamber combination is being moved by a camshaft, which is communicating with a main motor axle of said motor. If we use the data, which have been used for calculating the motor power, than the change in pressure of the inflatable sphere piston may be done by changing the volume of the enclosed space of said actuator piston, by changing the volume 'under' the classic piston. The volume change per piston per stroke needed by the actuator piston from a second to a first longitudinal position, thus from a small sphere shape (ø 25,1 mm) with a medium internal pressure (3,5 Bar) to a bigger sphere shape (ø 46,9 mm) with a low pressure (0,5 Bar), with a constant volume of the enclosed space is done by the internal pressure change of said actuator piston. The Force is 260N/stroke/piston, irrespective the internal force, thus with 8 chambers, each comprising 5 pistons, and with 3 revolutions per second, the generated power is: 4,4 kW.

In order to come from the first to the second longitudinal position the energy needed is (Fig.l4A and 14B):

1. change the sphere shape (ø 46,9mm; 0,5 Bar) of the actuator piston to its production shape (ø 25,1 mm; 0 Bar (overpressure)), by deflation of the actuator piston into the enclosed measuring space, which is now increasing volume - this may be cost no energy, if the friction forces between the pump piston and the wall of the enclose space are small enough,

2. to inflate the sphere (ø 25,1 mm, 0 Bar) to (ø 25,1 mm, 3,5 Bar), by decreasing the volume of the enclosed space, where a pump piston is coming nearer the actuator piston - the energy needed is:

Wisothermai = -1 x 8280 x 2,302585 x log 4,5 = 12454 Nmm/channel/piston/revolution, and for 2x4 chambers, 5 actuator pistons per chamber, 3 revolutions per second. = 12,5 x 8 x 5 x 3 Js= 1,5 kW.

(* P₂ absolute is 4,5 bar, if Pi = 1 bar absolute).

Thus: generated brutto power is 4,4 kW and needed power for getting the motor run is at least 1,5 kW, thus approx. 2 kW necessary, besides eventual other losses.

In order to access the motor, if a pump complying to the above mentioned should be present in a car, we compare it to what is available: a present compressor has the following specification 220V, 170 1 min, 2,2kW, 8 Bar, pressure storage vessel 100 1. We need the power, but at a lower pressure, so that this modified compressor is a bit quicker charging the pressure storage vessel. P = 2200 W for 8 Bar, hence for 3½ bar may be needed using the same repressuration time as for 8 Bar) only 3/8 x 2200 = 825 W. Even if a battery is a 24V battery, the current will be 825/24 = 34,4 A - this is very much for a battery, and consequently would many batteries be available, in the motor configuration Figs. 11A,B,G and Figs. 12A, 13A, that the pump with reference numbers 826 / 831 should be electrical. Charging these batteries would only be possible by an external power source, so that a car should be ineffective during many hours - the capacitator solution (Fig. 15E) is still in its research phase - this would not be a preferred embodiment, but an optional.

It may be better to avoid a conversion of power, and to use the motor configuration of Fig. 15C where the pump 826 / 831 is communicating with the axle of a combustible motor, using e.g. H₂, which has been generated by preferably electrolyses, and optionally by a fuel cell. The last mentioned process is powered by electricity from a battery which is charged by an alternator, which is communicating with said axle.

The 825 W needs to be generated by said combustible motor - this may be a 24cc / 66cc (VW Golf Mark II has motor of 53kW, 1600cc, ø 90mm, 4 cylinder → 825W is approx. 24cc, 90mm one cylinder or if 3x faster: 2,2kW is approx. 66cc, 90mm one cylinder) classic motor, using the Otto cycle, which may be compared with a big currently used moped motor. A moped has been shown on television for a couple of months ago, using a electrolyses of water, stored in a tank (originally for gasoline), and using the generated H₂ for the combustion process - this is feasible. For a car is this size of external motor indeed an auxiliarly motor - all extra combustible equipment, which we earlier had thrown out of the VW Golf Mark II to gain lower weigth, needs to be replaced by comparable equipment of a moped motor, which is regrettably necessary - no pollution or C0₂ emission, and the noise may be successfully reduced by proper noise reducing measurements, and the weight is only an assume 1/6 (= approx. 35 kg) of that for a car and a tank of 15 1 water = 15 kgs. - still may this feasibility study hold.

END 19627 amended 19611 added matter to the description - feasibility study in 19618

A further development may be that the inflatable piston is moving in a specially designed chamber, so that the generated force of the piston has been maximized, with a minimum of expansion (= pressure drop). And, that the interrupted movement, or 'hesitation behaviour' (please see page xx) of said piston may be compensated by an amended internal shape of said chamber.

Controlling said motor according to said first principle according to Fig. 1 A is a new aspect as well - for one actuator piston-chamber combination per crankshaft is this as follows.

It is assumed that the pressure storage vessel may have been pressurized by an external pressure source once and for all, thus at the production of the motor. Said actuator piston may start by means of an electric starting motor, using the battery, which has been charged by the solar cells, and/or by a classic dynamo, which is turned around by the main axle of said motor. Said starting motor is initially turning the crankshaft, and as a consequence of that movement said actuator piston is being pressurized internally - the pressurization of the actuator piston will thereafter take over the initiative of the movement of said actuator piston, and consequently the initiation of the turning of said crankshaft. Said starting motor may then be decoupled from said crankshaft.

It may also be possible that the motor is starting by means of opening up the pressure storage vessel 814, so that fluid 822 is pressurizing said actuator piston internally, which is initiating the movement of said piston - please see Fig.1 B.

Speeding up said motor, that is to say, speeding up the rotation of said crankshaft may be done by raising the pressure inside said actuator piston, by means of opening up a so-called reduction valve between said pressure vessel and said actuator piston in the (lead) line [829]. Slowing down the rotation of said crankshaft may be done by reducing the pressure inside said actuator piston, by closing down the opening of said reduction valve.

In order to give the motor more power (torque on the main axle) may be done, by increasing pressure for an existing configuration of actuator piston-chamber combination, or there may be more than one actuator piston-chamber combination per axle. Stopping the motor may be done by totally closing said reduction valve in said (lead) line [829]. Said reduction valve may be commiuncating with a speeder.

The pressure management in more detail of said actuator piston may be organized as follows. Both in the wall of the crank of the crankshaft and at the end of the piston rod may be holes, which communicate with a second and third enclosed space, and the enclosed space, respectively. At a certain point of time may these holes communicating with each other, so that the enclosed space of the actuator piston may be communicating with the second or the third enclosed space within the crankshaft - while communicating with the second enclosed space, the piston may then be pressurized through its enclosed space and may be moving from a second to a first longitudinal position in the chamber. While communicating with the third enclosed space, deflation of the piston may occur when the piston may be moving from a first to a second longitudinal position. The main piston pump (818) initiates the decrease of pressure in the third enclosed space in the crankshaft and the decrease of the pressure in the enclosed space in the piston rod, due to the interrelated default positions of the crankshaft of the pump, and of the crankshaft of the actuator piston, respectively, which may be assembled on the same axle.

More in detail may the pressure management of said actuator piston working as follows.

At the final second longitudinal position of the piston may the hole

FILL IN

More than one actuator piston-chamber combination in said motor may be present on the same axle. This concept however may not be helpfull complying to said specifications. As it is with current combustion motors, more than one piston-chamber combination per axle may make the motor running more smoothly. And, of course, the torque will be increased on said axle.

HOW IS IT RUNNING AND HOW IS THE INTERRELATIONSHIP BETWEEN THE ACTUATOR PISTON/CHAMBER COMBINATIONS PER ONE CRANKSHAFT ORGANIZED??

The crankshaft itself may be an inefficient way to generate rotational motion, and moreover, the stroke length of this type of piston-chamber combination may be larger than that of e.g. a current combustion motor - that is to say, that the r(otation)p(er)m(inute)'s of said crankshaft may be substantially lower than that of a current combustion motor. A gear may be necessary, and the gearing ratios may be different from that of current combustion motors. The gearbox may reduce the efficiency with say 25%, and said efficiency may be improved (by say 50%) by using low friction bearings such as Fluid Dynamic Bearings. As the motor may run the whole time, a clutch may be needed. Thus the 33.2% of energy needed for a car motor should come from e.g. green energy, e.g. solar energy from e.g. solar cells on the roof / hood of the car / the paint of the whole body, and that may be too much. Of course could there be added some special batteries, if these are being charged with energy from wind power or solar energy - this adds to the dead weight of a vehicle and increases the WTR ratio - the last mentioned would partially need a distribution structure. Thus, this motor type may not fully complying to said specifications, when one would aim e.g. a 'green' car motor. Thus, in order to complying to specifications a crankshaft may be avoided, as well as a gear.

ROTATING POWER SOURCE FOR A 'GREEN' MOTOR based on the principle of Fig. 2A

This bring us to the point where said piston may be rotate instead of translate - this new type of motor may be a kind of a 'green' Wankel Motor.

Al

A still better use of energy may be obtained by a motor without a crankshaft, using the same principle as above mentioned, at least for the propulsion system. Besides the foregoing mentioned, may this decreased use of energy specifically be obtained in a chamber around a circleround centre line, which may be concentrically positioned around the main axle of said motor, by reducing the distance from a 1^st rotational position to a 2^nd rotational position of a piston in said chamber to approximately the radius of said piston, so that the motor almost continuously may be powering said axle.

Al

A conical chamber, wherein a piston may function as a self-propelled actuator, may be bended circularly in the longitudinal direction, and may be filling 360° or a part of it. There may be at least one piston functioning in said chamber. The motor may comprising one of more actuator piston-chamber combinations, which may be using the same axel. In the center of the circular motion of said actuator piston and/or said chamber may be an axle, which may be connected to the construction elements which makes a car or another vehicle run, such as wheels c.q. a propeller.

There may be two ways to construct such a motor. One is, to have the centre axis of the actuator piston rod moving in the plane where the centre axis of said chamber lies. Another possibility may be that the centre axis of the actuator piston rod may be positioned perpendicular the plane where the centre axis of the chamber lies. In both cases may said actuator piston moving or the chamber, or both. Running an actuator piston like the one which was used in the elongated conical chamber - an ellipsoide to sphere and vice versa formed piston (e.g. WO2000/070227 - Figs. 9A,B,C) in a circularly bend chamber seems unlikely, as the chamber may be circularly bend in its longitudinal direction, so that the bearings of the piston rod of said actuator piston are missing.

Instead, a (smaller) sphere to (bigger) sphere and vice versa type actuator piston may be used (e.g. WO2002/077457 Figs. 6A-H, 9A-C), which due to its symmetrical form enables a less complex construction for the bearings of the piston rod. E.g. the- piston rod may be positioned through said actuator piston perpendicular to the plane where the centre axis of said circularly formed chamber lies.

Said actuator piston may be moving in said chamber, because of the fact that said chamber is identically shaped as the straight chamber which was used when using a transitionally moving piston, but now, circularly.

However, the size of the part of the wall of said piston which lies behind the transitional centre axis of said piston perpendicular the centre axis of said chamber, and a direct line from the centre of the piston to the place where chamber and piston engaging (or sealing or both), is substantially smaller than that of the ellipsoide <→ sphere piston which is translating on the centre axis of an elongate chamber. That is why the assumed power which each actuator piston (sphere - sphere) has, may be less than of a ellipsoide <→ sphere actuator piston. This calls for a motor, where more than one actuator piston per chamber is being used. Additional issues call for the same, because the actuator piston is moving interruptedly (please see later), and more than one piston in the same 360° chamber, may create a smooth motion. And, when said actuator piston(s) having expanded to its maximum, a very short moment occurs, that the pressure within said actuator piston is decreasing, and this may also give a 'moment of hesitation' in the motion - in order that one actuator piston is overcoming 'hesitations' in the motion of another actuator piston, said actuator pistons may be positioned on different positions on the centre axis of said chamber. As an example, if the 360° chamber has been updivided in 4 identical subchambers, the number of actuator pistons may be five, equally divided over the 360°.

The major advantage of such a rotational motor may be, that the length of the return stroke of an actuator piston from a 1^st circular position to a 2nd circular position has been substantially reduced in comparison with the crankshaft option and may be at least the size of the biggest radius of the piston at a 1st circular position, because the circular 1^st position and the circular 2^nd position are in direct continuation of each other in the direction of rotation.

Thus the drop of pressure inside said actuator piston and the raise of pressure immediately thereafter may need to be managed.

There may be two fundamental ways to do change the inside pressure of the actuator pistons. One option is that each of the actuator pistons may be connected by a channel to a valve which may be able to increase / decrease the pressure in said actuator pistons. Said valves may be computer steered, so that the pressure inside each actuator piston is optimal to its position in said chamber. Additionally may be accomplished that said computer is steering the pressure from a pressure vessel, which is serving as a pressure source, so that the distribution of the available pressure in each of the actuator pistons may optimize the use of the available fluid pressure for said actuator pistons. A second option is e.g. by a very short change in the volume of the enclosed space. This change may be done by a movable piston which is sealingly connected to the wall of e.g. an elongated chamber. Said chamber may very well be of the kind having differing cross-sectional in the transitional direction. Because of the speed of the movement may this chamber be of a kind having a constant circumpherence, so that the piston only is bending during operation. But of course, chambers having differing sizes of the transitional circumpherence may also be an option. A piston moving within said chamber may have a piston rod, which may be communicating with a camdisk, which may be connected to the axle on which the motor is mounted. At the end of a piston rod may be a wheel, which is rolling over said camdisk. Thus, as such is this motor type not consuming fluid, only the contained energy (pressure) of said fluid.

The 360° chamber may turn around an axle, of which centre axis may be crossing the centre of said chamber. Said chamber may be part of a wheel, and the outerpart of said wheel may have a notch, in which a drive belt, which may be driving auxiliary devices, such as a electric generator.

Clearly is the type of motor where the chamber is rotating and the piston(s) non-moving the less complex solution of the two options of rotatable motors. Also is the generated torque better, e.g. 5x in said solution, because there are 5x more pistons per chamber of the same dimensions. The most reliable system may be a fixed piston in a rotating chamber. An advantage may be, that the motor may be comprising more than one piston, e.g. 5 pistons, which each may be positioned at different rotational positions, which may make the motor turning smoothly, because the transition of a piston from its 1^st rotational position to its 2^nd rotational position may be powered by e.g. 4 other pistons. And the "hesitation behaviour" (please see later) of a piston while moving from a 2^nd to a 1^st rotational position may be also supported by e.g. the 4 other pistons, so that no "hesitations" may being observed. A gearbox may be unnessary, as the pressure rate of the fluid inside the piston will define the speed of the main axle - this necessary pressure window may easily be obtained by the construction of this motor, while this pressure may easily be defined by a speeder. Thus a gearbox may be superfluously and that adds to a further weight reduction of approx. 50 kg. The VW Golf Mark Π conversion has now been additionally reduced to approx. 350 kg. The TWR is now approx. 5,6.

Controlling the rotational motor may be done in a similar way as the controlling of the motor with translating pistons (or even with translating chambers and non-moving pistons, or even when both are moving - not shown).

Controlling means: putting into function, starting up, speeding up, slowing down, powering up, stopping, and taking the motor out of use.

Putting the motor into function may be done by en electrical on/off switch, which is switching on the electrical system, and another switch which is connecting the starter motor to the electricity circuit, so that it is connecting to the axle, and turning.

On the same axle as the moving piston or moving chamber is using, may there be a starter motor, which is using electricity from a starter battery, which itself is loaded by electricity from a solar energy. The starter motor may be turning said axle, and so initiate the rotation.

FILL IN

The pressure management may be done as follows.

A In the motor where the piston is moving, needs this piston to be pressurized, and so that pressure is changing at the transition point where the biggest circumpherence is changing to the smallest. This may be done electronically by means of a computer and injection jet. As the pressurized fluid needs to be sustained, said solution needs a new solution.

NEW electronic/mechanic SOLUTION

Otherwise, would it be possible to create a mechanical solution, as the change of pressure is of a certain frequency: e.g. a camshaft, which is communicating with the drive shaft through a time belt. The camshaft may be pressing a flexible membrane which is communicating with said fluid, of which the pressure needs to be managed.

In order to make this solution less complex, may the chamber comprising one instead of e.g. 4 sub- chambers, so that the pressure needs to change only once. AA

In the motor where the chamber is moving, needs the e.g. 5 pistons to be pressurized, and so that pressure is changing at the transition point where the biggest circumpherence is changing to the smallest. This may be done electronically by means of a computer and injection jet. As the pressurized fluid needs to be sustained, said solution needs a new solution.

NEW electronic mechanic SOLUTION

In the motor where the chamber is moving, need the inside pressure of e.g. 5 pistons be managed differently from each other, but in the same order, and that pattern repeats itself for every turn, so that also here a camshaft solution may be possible: a camshaft which is communicating with the drive shaft through a time belt. The camdisk may be pressing a flexible membrane which is corrimunicating with said fluid, of which the pressure needs to be managed per piston. TRANSLATION AL POWER SOURCE for a motor based on the principle of Fig. 1 IF B

A still more reliable system may be obtained by a new principle according to Figs. 1 IF and 13F for the pressure management, namely by separating the fluid in the piston and the enclosed space, from the fluid in the repressurization stages - the change of pressure in the piston may be obtained by a change of volume of the enclosed space of the piston. The improved reliability may relate to reducing the number of transitions of pressurized fluid, which may leak. In this principle may mainly the controlling devices be using energy for changing the volume of the enclosed space. This may very well be done so that also here energy is being reduced, by using again a piston (e.g. one for the function of said piston, and preferably one for the speed/power - optionally a separate piston for the power management) which is moving sealingly in a cylinder, said cylinder having continuously differing transitional cross-sectional area's and e.g. changing circumferences so that again a 65% reduction of the energy used may be obtained. Also for this principle may the embodiment with a fixed piston in a rotational chamber be the best option for reducing the use of energy. Constant circumferences may also work, but the gained reduction may be lower.

B

The change (and consumption) of pressure of a fluid within an inflatable piston may also be done in an alternative way, alternative to the principle shown in Fig. 11 A. By temporary changing the volume of the enclosed space of said piston, while an adjustment of said volume may give a change in the power (torque) of said motor, and this may be done serially of simultaneously. The energy is coming from This is still a more efficient way to use the available energy, and it may increase, the reliability of said motor in relation to the principle of that shown in Fig. 11 A. There will in this new principle be no leaks between high pressure fluid when the piston is moving from 2^nd to 1^st longitudinal positions, and low pressure fluid when the piston is moving vice versa in the joints, such as crankshaft - big end bearing, and the two parts of the connecting rod. The energy used may be used to move a piston in a conical chamber which may be optimized to reducing the working force on the piston rod of said piston, for changing the volume of the enclosed space. Additionally is the energy used may be used in a similar piston-chamber combination as the one used for said volume changing, for adjusting the volume of the enclosed space.

The movement of the volume changing piston may be done by using pressurized liquid which is moving a piston in a chamber from one point to another an vice versa by means of e.g. valves or other land of control devices, or by magnetic guidance. This is also valid for the piston which is adjusting the volume of the enclosed space - the control of the movement of said piston may be done by communicating with a speeder, which is controlled by e.g. a person or a computer.

ROTATING POWER SOURCE FOR A MOTOR based on the principle of Fig. 13E

The change (and consumption) of pressure of a fluid within an inflatable piston may also be done in an alternative way, alternative to the principle shown in Fig. 12 A. By temporary changing the volume of the enclosed space of said piston, while an adjustment of said volume may give a change in the power (torque) of said motor, and this may be done serially of simultaneously.

This prin- ciple is in rotating power sources still more efficient than for transitional power source systems, because the distance from 1^st to 2^nd rotational positions is almost nil - therefore may the piston which is changing the volume of the enclose space be guided by a cam disk, which may be mounted on the axle, around which the motor power source is rotating.

In fact this is the most efficient motor.

A motor with a circular chamber may comprise a wall, at least a part of the length* of the centerline of said chamber, which is parallel to the centre axis of said chamber. In a motor may a conical chamber( elongate or circular*) be of a type where the force of the piston rod, generated by the actuator piston, is constant. That may also be the case for any of the pumps which are incorporating in said motor, where a fluid is pressurized. The chamber in which said actuator piston is positioned may be comprising internal convex shaped walls of longitudinal cross-sectional sections near a first longitudinal position, said section may be updivided from each other by a common border, a distance between two following common borders define the height of the walls of said longitudinal cross-sectional sections, said heights are decreasing by an increasing internal overpressure rate of said piston, or in the direction from first to second longitudinal positions, the transversal height of the cross-sectional common borders may be detennined by the maximum work force, which be chosen constant for said common borders.

In case the piston is positioned in a cylindrical chamber with an internal tapered center, said convex shaped walls are concave shaped.

And, said piston-chamber combination may comprise a wall of a cross-sectional border which is parallel to the centre axis of said chamber.

And, said piston-chamber combination may comprise a transition between said convex shaped wall and said parallel wall, where said transition may be comprising at least a concave shaped wall, which may be positioned near a second longitudinal position. And, said piston-chamber combination may comprise a concave shaped wall which may be positioned at least on one side to a convex shaped wall.

The various embodiments described above are provided by way of illustration only and should not be construed to limit the invention. Those skilled in the art will readily recognize various modifications, changes, and combinations of elements which may be made to the present invention without strictly following the exemplary embodiments and applications illustrated and described herein, and without departing from the true spirit and scope of the present invention.

All piston types, specifically those which are containers with an elastically deformable wall may be sealingly connected to the chamber wall during its move between longitudinal positions, engagingly connected or not connected to the wall of the chamber. Or may be engagingly and sealingly connected to the chamber wall. Additionally may there be no engaging between said walls either, possibly touching the walls each other, and this may happen e.g. in the situation where the container is moving from a first to a second longitudinal position in a chamber. The type of connection (sealingly and/or engagingly and/or touching and/or no connection) between said walls may be accomplished by using the correct inside pressure inside said container wall: high pressure for sealingly connection, a lower pressure for engagingly connection and e.g. atmospheric pressure for no connection (production sized container) - thus, a container with an enclosed space may be preferred, because the enclosed space may be controlling the pressure inside the container from a position outside the piston.

Another option for an engagingly connection is thin wall of the container, which may have reinforcements which are sticking out of the surface of said wall, so that leaking may happen between the wall of container and the wall of the chamber.

In the case of an actuator piston, which is connected to the main axle by a crankshaft, and there are more than one actuator pistons present, all connected to the same main axle, the advantage may be that the turning of said main axle may be more smoothly, if the longitudinal position of said actuator pistons is different from each other, so that the "hesitation moment" for each of said actuator pistons, when moving from a second to a first longimdinal position, may occur on other points of time.

It may be necessary that all of said actuator pistons are engagingly or sealingly ( this may be different from a longitudinal position to another longitudinal position when moving in said chamber) moving from a second to a first longitudinal position in a chamber and vice versa, which has the characteristics that the force on the piston rod - thus the connection rod from the actuator piston to the crankshaft - may be independent of the position which the actuator piston has (please see the description and drawings with referent "19620"), in order to synchronise the force of each of said actuator pistons to said main axle.

The feasibility study until now did not incorporate quantitatively the lack of heat generated by a motor of the invention, in comparison with Otto Motor types.

When we incorporate heat loss, than the motors of this invention are still more interesting and convincing. Heat losses give a current Otto Motor an efficiency of 25%. ^"When we assume in the first instance that said motors of this invention do not generate heat at all, than it is possible to reduce the energy used to pressurize the fluid from 5 Bar to say 10 Bar (10 Bar was already present in the pressure storage vessel, when the motor was produced) by approx. 65% reduction.. The total efficiency of a motor according to this invention will then become under 10%, namely 8,75%, by the self-propelling actuator piston, and this is up to now unprecedented ( David JC Mackay, Sustainable Energy - without the hot air). When the pumps for regenerating pressure, shown in this invention, again are using the piston-chamber combination types according this invention, than another 65% of energy is saved. Thus this would give a total energy use of 8,75% x 0,875 = 7,6%, if we would disregard that heat is being generated by the pump. However, when a part of the energy used for pumping may come from another source, such as solar energy (photovoltaic), from a flywheel or from regenerative braking devices, than the total used energy still may end under 10%.

19618 amended 19611 added matter to the description - feasibility study

The feasibility study until now did not incorporate quantitatively the lack of heat generated by a motor of this invention, in comparison with Otto Motor types.

When heat loss may be incorporated, than the motor types of this invention are still more interesting and convincing. Heat losses may give a current Otto Motor an efficiency of 25%. When it may be assumed in the first instance that said motor types of this invention do not generate heat at all (isothermal), than it may be possible to reduce the energy used to pressurize the fluid from 5 Bar to say 10 Bar (10 Bar was already present in the pressure storage vessel, when the motor was produced) by approx. 65%. The total efficiency of a motor type according to this invention may then come under 10%, namely 8,75%, by the self-propelling actuator piston, and this is up to now may be unprecedented (David JC Mackay, Sustainable Energy - without the hot air - 2009). When the pumps for regenerating pressure, shown in this invention, again are using the piston-chamber combination types according this invention, than another 65% of energy may be saved. Thus this may result in a total energy use of 8,75% x 0,875 = 7,6%, if we would disregard that heat is being generated by the pump. However, when a part of the energy used for pumping may come from another energy source (than from the total motor power), such as a battery, charged by e.g. solar energy (photovoltaic) and/or a fuel cell (e.g. a H₂), from a flywheel or from regenerative braking devices coupled to a generator, than the total used energy still may end under 10%.

Earlier has already been concluded that the configuration of a motor type according to Fig. 1 IF and Fig. l3F may be the most efficient (simple construction, almost isothermal thermodynamics), and may additionally be the most reliable (no leaks), and of which the configuration of Fig. 13F is without the use of a crank generating rotation, will the configuration of Fig. 13F be used in a quantitative assessment of a car motor.

We use a current VW Golf Mark II model RF, 1600cc, weight 836kg, with a 53 kW / 71 pk gasoline motor, comprising 4 cylinders of each ø 81mm, and a pressure of 9 Bar, and a stroke of 77 mm as a benchmark for the invention. This gives a max. force of 1159 N per cylinder, which is approx. 116 kg per cylinder. A weight reduction of approx. 50% may be assumed, if all the combustion parts would be taken out of the car body, and aluminium would be used instead of steel for said body. Thus necessary may be 58 kg per cylinder to drive an aluminium body, up to 4 passengers and luggage. The chamber of the pump shown in WO2008/025391 has a max. working force of 260N (26 kg), over approximately the whole stroke of 400mm from 2 - 10 Bar, and with a diameter of ø 58mm - l7mm, respectively. Using an inflatable ellipso^'ide shaped piston in this chamber, the actuator is functioning very well in practise. Thus, two of these chambers, now used as part of an actuator could be equivalent with one cylinder of the gasoline motor of said VW Golf Mark II, now made of aluminium, and all parts related to combustion taken out.

The change of the volume of said sphere may be quite big: from

4/3 x 3,14 x 23,45³ (ø 46.9mm; Pi=0,05 N/mm²) = 54015 mm³ - which is a AV of 6,5 and a ΔΡ = 7. The angle of the wall relative to the centre axis of said chamber is: Li=302,78 - 86,57= 216,21, Δτ= 10,9: angle = 2,9°- this angle is good.

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

W_isolhtrmai = 0,35 x 54015 x In 7= 0,35 x 54015 x 2,302585 x log 7 = 36788 Nmm/channel/piston/revolution 36,8 J/channel/piston/revolution, if there would only be one actuator piston per channel. Said motor according to this invention is not as quick as said gasoline motor (900 rev/m), regarding the number of strokes/minute - this is due to the assumed slower expanding and contracting of the actuator piston, which is made of reinforced rubber. Let us assume the number of revolutions/minute is 60, thus 1 per second ( 15x slower than said combustible motor). The W= 36,8 J/channel/piston/s. There are 2 x 4 'comparable' chambers (cylinders) - the power is than 294,3 J/s/piston, which is 0,295 kW/piston. When using 5 pistons, one in each of the 5 sub-chambers of each of said 360° channels (Fig. 13F), than may the generated power be: 5 x 0,295 kW = 1,47 kW.

Check of the assumption 1 revolution per second: a combustible gasoline motor amounting 53 kW, of which it was stated earlier in this study, that it may save 92,4%: 7,6% may only be used: 4,03 kW. That may firstly complying to the above mentioned calculation, if the number of revolutions per second may approx. be (rounded off): 3 revolutions/sec.

Thus, a motor comprising 2x4 'comparable' chambers, each comprising 5 pistons in 5 sub-chamber, rotating at 3 revolutions per second (= 180 rev/min.), resulting in a power of approx. 3 x 1,47 = 4,4 kW - this may be enough to drive a VW Golf Mark II with an aluminium body.

The literature (David JC Mackay, Sustainable Energy - without the hot air - p.127, Fig. 20.20/20.21) reveals a small electric car using approx. 4,8 kW power to run, and which is coming from 8x 6V batteries— that car could run 77 km on one batteries' charge, and charging time is several hours. If the energy is coming from batteries, which cannot be charged during the drive of said car, this may be an option, but not a preferred embodiment.

The energy may come from the kinetic energy from said rotating chambers, where e.g. the piston of a classic piston-chamber combination is being moved by a camshaft, which is communicating with a main motor axle of said motor. If we use the data, which have been used for calculating the motor power, than the change in pressure of the inflatable sphere piston, may be done by changing the volume of the enclosed space of said actuator piston, by changing the volume 'under' the classic piston.

The volume change per piston per stroke needed by the actuator piston from a second to a first longitudinal position, thus from a small sphere shape (ø 25,1 mm) with a medium internal pressure (3,5 Bar) to a bigger sphere shape (ø 46,9 mm) with a low pressure (0,5 Bar), with a constant volume of the enclosed space is done by the internal pressure change of said actuator piston. The Force is 260N/stroke/piston, irrespective the internal force, thus with 8 chambers, each comprising 5 pistons, and with 3 revolutions per second, the generated power is: 4,4 kW.

2. to inflate the sphere (ø 25,1 mm, 0 Bar) to (ø 25,1 mm, 3,5 Bar), by decreasing the volume of the enclosed space, where a pump piston is coming nearer the actuator piston - the energy needed is: W_isothermal = -l(check this) x 4/3 x 3,14 x 12,55³ x In 4,5*/l = -1 x 8280 x 2,302585 x log 4,5 = 12454 Nrnm/channel/piston/revolution, and for 2x4 chambers, 5 actuator pistons per chamber, 3 revolutions per second. = 12,5 x 8 x 5 x 3 Js= 1,5 kW.

(* P₂ absolute is 4,5 bar, if Pj = 1 bar absolute).

In order to access the motor, if a pump complying to the above mentioned should be present in a car, we compare it to what is available: a present compressor has the following specification 220V, 170 I/min, 2,2kW, 8 Bar, pressure storage vessel 100 I. We need the power, but at a lower pressure, so that this modified compressor is a bit quicker charging the pressure storage vessel.

P = 2200 W for 8 Bar, hence for 3½ bar may be needed using the same repressuration time as for 8 Bar) only 3/8 x 2200 = 825 W. Even if a battery is a 24V battery, the current will be 825/24 = 34,4 A - this is very much for a battery, and consequently would many batteries be available, in the motor configuration Figs. 11A,B,G and Figs. 12A, 13A, that the pump with reference numbers 826 / 831 should be electrical. Charging these batteries would only be possible by an external power source, so that a car should be ineffective during many hours - the capacitator solution (Fig. 15E) is still in its research phase - this would not be a preferred embodiment, but an optional. It may be better to avoid a conversion of power, and to use the motor configuration of Fig. 15C where the pump 826 / 831 is communicating with the axle of a combustible motor, using e.g. ¾, which has been generated by preferably electrolyses, and optionally by a fuel cell. The last mentioned process is powered by electricity from a battery which is charged by an alternator, which is communicating with said axle.

The 825 W needs to be generated by said combustible- motor - this may be a 24cc / 66cc (VW Golf Mark II has motor of 53kW, 1600cc, ø 90mm, 4 cylinder → 825 W is approx. 24cc, 90mm one cylinder or if 3x faster: 2,2kW is approx. 66cc, 90mm one cylinder) classic motor, using the Otto cycle, which may be compared with a big currently used moped motor. A moped has been shown on television for a couple of months ago, using a electrolyses of water, stored in a tank (originally for gasoline), and using the generated H₂ for the combustion process - this is feasible. For a car is this size of external motor indeed an uxiliarly motor - all extra combustible equipment, which we earlier had thrown out of the VW Golf Mark II to gain lower weigth, needs to be replaced by comparable equipment of a moped motor, which is regrettably necessary - no pollution or C0₂ emission, and the noise may be successfully reduced by proper noise reducing measurements, and the weight is only an assume 1/6 (= approx. 35 kg) of that for a car and a tank of 15 1 water = 15 kgs. - still may this feasibility study hold.

The motor based on a crankshaft solution (Figs. 11A-D and 1 IF) with an elongate chamber and a piston which is connected to said crankshaft by a piston rod / connection rod, may preferably be used as a main motor of a transport vehicle, e.g. a car. Said wheels or propellors may be connected to the central main motor by drive shafts and a distibution device such as a cardan. Optionally may said motor type be used as a decentrally positioned motor, which may be directly connected to each of the propulsion devices, such as wheels or propellors.

The motor based on a chamber which is positioned around a circleround centre axis and a piston which is increasing and decreasing its size (Figs. 12A-C, 13A-G), may preferably be used as a decentrally positioned motor in a transport vehicle, e.g. a car. Each of said motors may be directly connected to each of the propulsion devices. Optionally as a central motor, which may be connected to said propulsion devices by driveshafts.

The control of said motors may preferably be done by a computer, specifically when each motor is directly connected to one of more than one propulsion devices which a transport vehicle is using.

A flywheel which may preferably be connected to a main central motor, and optionally decentrally positioned to each of the propulsion devise. A flywheel may be used for keeping the motion smoothly - the classic solution - or to regaining energy for acceleration, after braking (and simultaneously storing the kinetic braking energy) of a transport vehicle - or to give energy to one of the pumps (e.g. references 818, 821,821 ', 826, 826' in Figs. 11A,B,C, F, 12A,C, 13 A,B,E,F) which are communicating with a pressure storage vessel (e.g. references 814, 839, 890, 889). All or a few of said types of flywheels may be present in a transport vehicle, which is comprising a motor according to this invention.

Another aspect of the regaining energy while braking may be pumps which are directly connected to a main axel, which may be a central driveshaft (e.g. references_. 821, 821 '), which may pump the fluid to a much higher pressure and communicate the resulting high pressure fluid to a pressure storage vessel (e.g. references 814, 839, 890, 889). 19617 optimal configuration of chambers for actuators in 19618

The geometry of chambers to be optimally used in co-operation with an actuator piston may be different from those, which are aiming an optimal use of a pump, because the conditions for the use in said actuator and said pump may be different.

For example the actuator piston needs to give a maximum force, by using as less energy as possible, while moving at an appropriate speed. And, for an actuator piston which is communicating with a crank, the sub-conditions may be different from the sub-conditions of e.g. an actuator piston which is communicating with a rotating chamber: e.g. the point of time where the maximum force is being needed.

In order to use the actuator piston as a self-propelled piston, it is necessary that an elongate chamber is of a type where the wall of said chamber is widening outwards when moving from a second to a first longitudinal position. Thus, the angle of the wall in relation to the centre axis of said chamber, from a second to a first longitudinal position needs to be positive. This angle may be fixing the speed of the actuator piston. And of course need the transitions from one point of the wall to another in the longitudinal direction be smooth, so as to limit friction between said actuator piston and said wall of the chamber.

The inflatable actuator piston itself needs to have an internal pressure in order to be able to load the wall of the chamber. In order for said actuator piston to be able to move needs the centre of the flexible wall be closer to a first longitudinal position than the circumference which is engagingly connected to the wall of the elongate chamber. The larger this distance is, the higher the speed of said actuator piston in said chamber.

The reaction force of the wall of the chamber on said actuator piston is fixing the force which with the piston is pushing itself off the wall of the chamber in the direction of a first longitudinal position. Thus also the force on the piston rod, if at least one cap of the actuator piston, best nearest a second longitudinal position, is assembled on said piston rod.

In section 19620 of this patent application is a chamber shown (e.g. Fig.21A), which, when used in a pump, reduces the working force on the piston rod with approx. 65% at 8- 10 Bar of the pumped fluid - this is excellent for pumping purposes. This reduction should be seen in comparison with the force needed in a straight cylinder, and comes from a comparison of a classic high pressure bicycle pump, and an advanced bicycle pump where the chamber has the shape of Fig. 21 A. In said chamber is the maximum force approximately independant of the pressure of the fluid in said chamber, thus approximately constant (e.g. from 2 Bar, when the maximum force has been reached) during a pumping stroke.

An identical chamber used in an actuator, comprising an actuator piston, may have the advantage that the force is approximately constant during the stroke from a second to a first longitudinal position - the price to be paid may than be that the working force may only be approximately 1/3 in relation to the working force when the maximum pressure has been reached in a straight cylinder having a certain diameter (same comparison source as mentioned above). The size of the force may not be appropriate for the purpose of an actuator piston, while additionally the force, being constant, may not be appropriate either in relation to the use with a crank.

The same may be valid if the chamber is circleround ('circular') instead of elongate. In the particular solution where an actuator piston is non-moving, and positioned in a rotational moving chamber may such a chamber type as mentioned above be used. If more than one piston is used, e.g. 5 pistons (e.g. Fig.1 OB), than such a chamber may be necessary, when each piston is at a different circular position in each sub-chamber, thus different pressure, the force derived by each piston may be the same for all pistons, so that none of said pistons is pushing others - the total force is 5x that of when only one piston would have been used. A gear may than be necessary to obtain the required torque, and speed, depending on the purpose.

Other optimal configurations of for actuator chambers may be possible.

The parameters for an elongate chamber of which the actuator piston is connected to a crank, may be:

• relative short length L of the chamber, so as to obtain a relative short stroke length,

· the force F(p,d^) may vary during the stroke from a 2^nd to 1^st longitudinal positions, so that the maximum force is obtained when the actuator piston is almost reaching the extremity of first longitudinal positions [where F= the force from the piston rod; p= the pressure inside the actuator piston; d= the diameter of the chamber at a certain longitudinal position; μ= the friction coefficient between the wall of the chamber and the flexible wall of the actuator piston], • the friction force Ρ(μ) during the entire return stroke is zero, which is obtained by lightly sucking out the overpressure of said actuator piston [Ρ(μ)= the friction force between the wall of the chamber and the flexible wall of the actuator piston],

• the velocity v(cp,F) should be optimised with the length L of said chamber [where v=speed of the actuator piston relative to the chamber; cp=angle between the wall of the chamber and the centre axis of said chamber; F= force from the piston rod],

• the energy used is as less as possible - thus: the pressure drop (AV) when the actuator piston is moving from a 2^nd to a 1^st longitudinal position, while changing its volume, while the enclosed space temporarely has been closed, needs to be as less as possible.

The parameters for a chamber of which its wall is positioned around a circleround centre axis, of which its center is positioned on the centre of the main motor axle, where said chamber is rotating, and where more than one actuator piston is present and non-moving, and being engaging said chamber wall, may be, additionally to said chamber of Fig. 21 A, having a circleround transversal cross-section:

• the circumference of chamber wall, irrespective the distance to the centre of rotation, needs to be identical - this may affect the shape of the transversal cross-section of said chamber

• the friction force needs to be optimally small, e.g. by using enhanced lubricators like Superlube which has a much smaller friction coefficient than other lubricant, and which is functioning well with rubber and metal, like steel or aluminium.

It may however be necessary to produce an optimal configuration of the piston as well to achieve the effect of that the circumference of chamber wall, irrespective the distance to the centre of rotation, needs to be identical, the circumference of chamber wall, irrespective the distance to the centre of rotation, needs to be identical -

19617 thermodynamical issues in 19618

When the fluid in the system (elongate chambers with a an actuator piston communicating with a crankshaft - chambers which may be symmetrically arranged around a circleround centre axis, which may be either communicating with a crankshaft, or with the main axle of a motor) is compressed, heat may very well be produced.

The storage of a fluid in a pressure storage vessel may have been arranged while the device, in which the motor is being used, was produced. While the motor runs, a smaller portion of heat may be generated in said storage vessel, when fluid of a higher pressure from the last pump of the pressurization cascade enters the fluid of said vessel, which may have a lower pressure (Figs. 1 1A-C, 12A-C, 13A-B).

The pressurization of the fluid which comes from the third enclosed space of a motor type which uses a crank, which is assembled on the main axle of said motor, generates a much bigger portion of heat in the first pump of the pressurization cascade, which may receive its energy from the main axle. And another portion of approximately the same magnitude of heat may be generated with a pump which may gets its energy from the other energy source(s) (preferably any sustainable energy source(s) such as solar cells, a fuel cell, electric batteries which have been loaded by solar energy or optionally a classic energy source, such as electric batteries, which are being loaded by a generator which is communicating with a combustion engine) (Figs. 11A-C, 12A).

In the actuator piston takes both pressurization in the enclosed space + the cavity within the actuator piston body from the second enclosed space, and expansion to the third enclosed space place. As the pressurization may be a bit more than the expansion, the actuator piston may get a higher temperature than its temperature when the motor started (Figs. 11A-C, 11F, 12A-C, 13A-E).

Thus this system is generating heat, which e.g. may be used for heating the cabin of a car, or to heat the third enclosed space, where expansion takes place (adiabatic). Because this is positioned in the crankshaft, it will not be easy to be done. Thus this may be more or less a diabatic situation.

Better of course is it to compensate the production of heat, there where it is being produced: the isothermal situation. In case the change of the pressure inside the actuator piston is being controlled by a piston which is moving in a chamber of a bi-directional pump - which is in fact an enclosed space of said actuator piston, both compression and pressurisation will take place in said chamber by changing its volume, so that heat and cooling may balancing: this may be the case with the combination of a non-moving actuator piston and a moving (rotating) chamber (Fig, 13F-G). Again, now with thermodynamic's aspect, is this the most efficient motor principle, because the (theoretical) efficiency may be near 100%.

19617 amended 19615 energy sources working together with the motor in 19618/19627

The motor may be working together with any other energy source, preferably sustainable, optionally non-sustainable. Such energy source may be necessary to feed the approximately 7.5% of the motor, which may be the limit of the efficiency improvement in relation to a classic motor burning fossile fuel, e.g. by using the Otto cyclus.

Sustainable energy sources like e.g. the sun, potential energy from water and wave power and other sources, which do not result in emissions of undesirable chemicals such as CO, C0₂, NO etc., when the energy has been generated.

For a motor according the invention may the energy source(s) preferably be e.g. electricity, a capacitator (= electricity stored in a very big condensator) or electric batteries of any type, charged by solar power through e.g. photo voltaic solar cells with or without focus means (mirrors), or by fuel cells e.g. using H₂, or air compressed by potential hydroenergy etc. An H₂ fuel cell may be 'charged' with H₂, which may have been derived from electrolyses of H₂0, which may be stored in a vessel - the electricity may come from a special battery, capable of giving continuously energy (no starter battery) - this battery may be charged by an alternator, communicating with an axle of said motor and/or from photo voltaic solar cells. The H₂ may also be stored in a special vessel, and may directly be inserted in the fuel cell.

Optional energy sources may be electricity, a capacitator or electric batteries of any type, loaded by an electric generator which is turning around on the basis of steam, generated by a fossil fueled burner, or a compressor driven by a motor, burning fossil fuel etc.

A motor according the invention may have one energy source or a combination of energy sources, preferably sustainable, optionally sustainable and non-sustainable.

When the motor is used as a motor in a transport device, such as ships, trains, cars or aeroplanes, which has limited possibilities to connect to big energy sources, the batteries may be temporary charged by an external energy source, e.g. through an electric cable. Filling up of other energy containing materials, e.g. H₂ may be done by hoses etc. Thus charging the energy bearing material positioned in said device by a temporary suitable connecting to said external energy source(s).

It may preferably be that said devices be able to move over such a strategic distance, where it is self-supporting without a longduring external fill up from an external available power source (e.g. electrical). A strategic distance may have several definitions, e.g. for a commuting car, 2x 50 km commuting + 40 km random per day may be enough without a refill, and e.g. a car used for traveling longer distances may need to travel 500 km without a refill, or even twice that distance. The last mentioned may be the limit for what humans may perform per day.

Preferably may a movable power source (e.g. a battery, a fuel cell, an electrolyses of H₂0 resulting in available H₂ for combustion purposes, pressurized fluid or other possibilities not mentioned here) which have been mounted in said transport device be self-supporting for at least one day. It may preferably also be possible to travel at night. Said power source may preferably not add very much to the extra dead weight (increasing the RAT), specifically important for cars, although this may not be decisive for the efficiency.

There are several battery types, and the newest are high power, are efficient, but add much to the extra weight and space. It takes a long time to charge these, while an rapid exchange of batteries is not feasible, as it demands an infrastructure, while one may not be able to separate new from old batteries. A charging from a and/or a solar cell may not be enough for the use of energy (see the feasibility study). It is necessary to have a plug, and a connection to the electricity network, which is an available infra-structure.

In order to reduce the charging time to 1-2 minutes, the 'battery' based on loading a condensator of the size of a suitcase, and release controlled the electricy again to the motor system may very well be the solution for all the problems mentioned above while using a battery. It is still under development in the USA.

A fuel cell may not be cheap, not very efficient to generate electricity, but adds not very much to the extra weigth, and it is n't noisy - this contrary the traditional method when a combustible (fossile) motor is communicating with a alternator - the e.g. necessary H₂ may be a security hazard, and storage of H₂ may be difficult, due to leaking from vessels, which for other matter are leak free. It may also need a distribution infrastructure, although there are already home based electrolyses systems on the market, which with electrolyses produces H₂ for own use. However, after having seen in 2009 a moped, with a combustible motor (<50cc), using H₂ from instant electrolyses of water, said water being contained in the tank where normally gasoline was stored, it may be possible to do this for this motor according to this invention as well. The electricity for the electrolyses may come from a battery which is designed to be used for equipment (constant use), and which may be charged by an alternator, using the rotational kinetic energy from said motor, while electricity is additionally charged by e.g. a solar cell.

The electricity generated by a fuel cell, e.g. using H₂, may be used to charge said battery, of which generated electricity may be used for the motor functions. An alternator may be communicating with the main axle of said motor, and additionally charge a battery, e.g. said constant use battery and a possible present start motor battery for a possible present start motor. Solar cells may add to charge said batteries. The electricity generated by a fuel cell, e.g. using ¾, may be connected directly to the motor functions, bypassing said batter(y)(ies).

Another possibility may be that e.g. H2 is being used for combustible purposes - e.g. a motor comprising a classic piston-straight cylinder combination with a crankshaft, turning an axle which is communicating with an alternator, said alternator being charging a battery. The alternator may also be directly connected by wires with the other motor functions. The power of said combustible motor may be complying to the complement need for power, thus what the motor according this invention cannot generate. The power of said combustible motor may be very small in comparison with current combustible motors when used for 100% for the motor functions, which makes it feasible that e.g. the eletrolyses process for generating H₂ may be made movable, e.g. to be used in a car.

What may be needed for the current invention is that a bi-directional pump, which is changing the volume of the enclosed space of e.g. the non-moving sphere piston, positioned in a rotating chamber may need electricity, if e.g. an electric motor may be used for turning around an axle which is communicating with a crank, on which the piston rod of said pump has been assembled. Said axle may be the main axle of said combustible motor using e.g. H₂ as fuel.

In another configuration, where said pump is used for a repressuration of a fluid, which is used to control an actuator, which is controlling said pump, it may have the same configuration as in the overall solution mentione above.

Another configuration may be used without using electricity for changing the volume of said enclosed space, when said pump has been exchanged by a camshaft - electricity may than only be necessary for a starter motor, and that may come from a starter battery, which may be charged by an alternator driven by the main axle of said motor, and/or by solar cells. A camshaft solution may preferably be using more than one piston, optionally one piston. A small pump may be necessary for speeding up, which means a higher pressure in the actuator piston, driven by the main axle or by an electric motor, which gets its energy from a battery, designed for constant use.

The tank, comprising conductive water may be filled up from an external storage of water, and, if the water is not conductive, it may be possible to add conductive material, so that the water is becoming conductive. The pressure storage vessel may be pressurized, not only by a cascade of pumps, but optionally also from an external pressure source, by a pluggable connection (ref. 2701 in the respective drawings).

The battery may be charged, not only by an alternator, solar cells or/and the H₂-fuel cell, but optionally by an external electric power source, through a pluggable connection. ( ref. 2700 in the respective drawings).

The piston and the chamber may rotate both around the middlepoint around which the chamber is rotating.

invention may be constructed with lighter weight than those based on the classic piston-cylinder combination. For at the motor may function in the dark, a complement or addition to the solar cells may be necessary. This may be e.g. any other sustainable power source e.g. a fuel cell, e.g. of a H₂ type which reacts with the 0₂ of the atmosphere, and giving electricity and H₂0. This fuel cell may need a relative small storage vessel, which may be of reduced pressure. This is to say, that the distribution system for h₂ may be at home, or that the distribution system may be not very dense.

In the motor type where an enclosed space is communicating with a repressurisation cascade of pumps, the electricity may be used to give energy to electric motor, which is driving the piston pump through another crankshaft - this may be done as a complement to the energy of the solar cells, e.g. when it is dark, or this may be done at any time.

Additionally may a generator been added to this motor type, which may be driven by the main axle, and which may load the accumulator.

In the motor type where the fluid in the enclosed space has been separated from the repressurisation cascade, possibly ore electric energy may be needed, for the control of valves. This may make the necessity of another sustainable power source, e.g. a fuel cell as described above, than the solar cells more likely.

It may also be used for an external cascade system, which has not yet been added to the drawings Fig 1 IF. and Fig. 13F, which may be needed for the repressurisation of the pressure vessel 1063, and 889, respectively. This may be done by a cascade of pumps, of which at least one is communicating with the main axle, and at least one with an external power source. The pumps may communicate with a pressure vessel. For the solution in Fig. 13F may a pump also be sufficient.

19617 gearbox - clutch in 19618

The motor according this invention may have a certain maximum for the number of revolutions per minute (rpm), which is limited by the change of shape and/or pressure at both turning points (first- and second longitudinal positions) when the piston is running in an elongate chamber, or when tunning in a circular chamber the change point from the first- to the second circular point. The flexibility of the inflatable piston is the key: its wall, which e.g. may be made of rubber - thus the hardness of the rubber - and the reinforcement layer, and how many reinforcement layers are being used, and, if used more than one layer is being used, the in between angle of the reinforcement layers - please see chapter 19650.

The motor according this invention is a two-stroke motor when a piston is running in an elongate chamber: one half revolution = power stroke, and the other half is the return stroke. When we compare it in the feasibility study with a four-stroke 4 cylinder 1595 cc VW Golf Mark II petrol motor, which has an idle speed of 700-800 rpm, and a maximum of 2500 (check) rpm, the comparable speeds of the motor according this invention may be half of the above mentioned, in order to generate the same power, with the configuration according the feasibility study. This reduced speed would suit the motor according this invention.

A reduced speed would limit the impuls of the main motor axle, when a clutch is starting to engage with the flywheel. In the feasibility study has we figured out the configuration of the motor, when having a comparable torque per kg weight of the car, in relation to the above mentioned Golf Mark II - the 50% reduction of net weight of the car according to this invention, cannot be taken into account now, if we keep said configuration.

If a gearbox (manual, autmatic - e.g. the Van Doorne's Variomatic^® or a common automatic gearbox with a fluid), is being used, the ratio's and the number of gears may be different from those in cars currently used. The last mentioned has to do with the specific characteristics (limitation of the functional window in terms of rpm of teh main motor axle) of a combustion motor, which is not present as the main part of the motor according the invention. The last mentioned would, if a gearbox would be necessary, preferably have an automatic gearbox, optionally a manual gearbox. Quantitative considerations may be as follows:

- wheel diameter: ø 0,65m (VW Golf Mark II),

- motor idle speed: 350 - 400 rpm - motor driving speed: 2x idle speed.

Thus: 60 km/h: motor: 750 rpm

wheels: 490 rpm thus: gear ratio: 1 :1,5 down

90 km/h: motor: 1000 rpm

wheels: 735 rpm thus: gear ratio: 1 :1,35 down

120 km/h: motor: 1250 rpm

wheels: 980 rpm thus: gear ratio: 1 :1,28 down 140 km/h: motor: 1500 rpm

wheels: 1143 rpm thus: gear ratio: 1 : 1,31 down

Conclusions:

• If no reverse traction was necessary, a gearbox may be unnecessary, and by that another reduction of weigth could be obtained.

• The rpm. seems still too high for the change of shape of the inflatable piston, and if that has been proved to be correct, a gearbox may be necessary - if so, the relatively slow turning motor may be needed to gear up its rpm., in order to be able to couple the motor to the wheels by a clutch; in order to be able to use these rpm. for normally sized wheels, it may be necessary to gear down again.

19617 motor sound in 19618

The sound pitch of the power part of the motor according this invention is of very little magnitude due to the lack of explosions, and that may make a big difference with the common well-know engine sound of petrol motors based on the Otto Motor design (please see Classiccars, issue no. 402, pages 86-89, February 2007, "Why engines sound so good" for prior art). Instead, there may be a sound of lubricated (e.g. Super Lube) friction of an inflatable rubber piston body on metal or plastic from the chamber - the sound may be of low frequency.

Only in the elongate chamber design will be a frequency of pitches of sounds (from second to first longitudinal positions) / silence (from first to second longitudinal positions), while there will be conttneously sounds in the circular chamber designs - as these also are friction sounds, the sound may be of low frequency.

Because the motor according this invention is a two-stroke motor (remember: a green one!) while most of the car motors today are four-stroke motors, the revolutions per minute in the motor according this invention may be half of that in a motor according the Otto design, in order to achieve the same or comparable power. Also this lowers the number of revolutions per minute which may add the sound to be of low frequency.

Additionally is there sound from a pump (compressor) which is generating the pressure for repressuration of the pressure vessel. When a pump is a piston-chamber type according this invention, it may give some noise from valves and noise from the release of fluid from the chamber to the pressure vessel, and the intake of depressurized fluid - according the type of motor repressuration according to Figs Current air compressors based on a piston moving in an elongate chamber sound absolutely ugly. These sounds may come from the fact that the speed of the air may be over the speed of sound, so that shock waves are the source of the ugliness.

In the design according this invention will preferably the speed of the fluid be lower than the speed of sound, optionally will a shock wave from an over air speed wave be damped, e.g. by contra wave designs (such as Audi did in its race cars, which were almost without noise, even the motor was a combustibel motor type). In the repressuration type according Figs there are no valves, and only extra piston chamber combinations, for deriving the pressure change. This motor type is besides being the most efficient, additionally the most quiet of all motor types according this invention. The generating of electric power for (re)loading a battery for powering the pumps, which may re- pressurize the pressure vessel, which may be serving the pressure for the main motor part, may need an Otto Motor of approx. 60 cc (comparable to a moped motor) on preferably H₂ as power fluid, optionally petrol/diesel or any other combustible fluid (please see the feasibility study). The sound of such a moped motor is normally ugly, but may be sounding acceptable, if sound dampened enough.

Thus, the total sound of the motor according this invention is not zero, such as is the case with an electric motor, but a low pitching low frequency sound. This enables the car to be identified by sound as being a car, which is better is this aspect than a car with only an electric motor running at low speeds.

The low frequency may be altered if it is concluded from a working prototype that the low frequency is that of the

19627 SUMMARY OF THE INVENTION

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

said chamber comprising a wall of a cross-sectional border which is parallel to the centre axis of said chamber.

[ said chamber comprising a second chamber, which is communicating

with said first chamber through a channel comprising a longitudinal

cross-sectional section o which the wall is concave shaped, the wall

of said second chamber is parallel to the centre axis of said chamber.]

The conical chamber of e.g. an advanced bicycle pump may be updivided into longitudinal cross-sectional sections of which its common borders are defined by an over pressure (e.g. over the atmospheric pressure) rating such as e.g. 1 Bar, 2 Bar 10 Bar which a piston may produce, while moving from a first to a second longitudinal position of said chamber. Said chamber comprising convex and concave shaped sections of longitudinal cross-sectional sections, said sections are updivided from each other by common borders, the resulting heigth of the walls of said longitudinal cross-sectional sections are decreasing by an increasing overpressure rate, the transversal length of the cross-sectional common borders is determined by the maximum work force, which is chosen constant for said common borders, at least near a second longitudinal position.

Another factor which is decisive for the proper shape of the longitudinal cross- section of said chamber, regarding proper sealing of the piston to the wall of the chamber, in a bottom position (a 2^nd position) of the piston, is that, there must be enough space to have the piston at that position and allowing it to move, e.g. when the chamber has been designed for lowering working force: the smallest longitudinal cross-sectional area at the point of the highest pressure: e.g. WO/2008/025391, where the smallest part of the chamber was ø 17mm.

The longitudinal cross-sectional sections may have convex and/or concave sides. The part of the chamber where convex shapes end and where a concave wall part is beginning, and which is matching a cone shaped bottom part, is used in a bicycle floor pump for the purpose to keep the convex / concave shaped part of the chamber on a certain ergonomical height, so that pumping is comfortable for the user (WO/2008/025391). A spring-force operated piston, e.g. a flexible expandable inflatable container piston (e.g. EP 1 384 004 Bl) may begin to move by itself from a second longitudinal position to a first longitidinal position in said chamber, where the cross-sectional area and circumference of a second longitudinal postion is smaller than the cross-sectional area and circumference of a first longitudinal position, if a sealing pressure exists from the piston to the wall of convex / concave chamber walls, and if the longitudinal component of the friction force between the piston and the wall of the chamber is lower than the longitudinal component of the sealing force. In order for the piston rod to maintain its position controlled by a user of e.g. a bicycle pump, it may be necessary that the wall of the chamber which is in contact with said piston, is parallel to the central axis of the chamber. This parallellity provides a sealing force without a longitudinal component, and so remains the piston which is sealing to the wall of the chamber in a position only there, where the user wants it to be. E.g. EP 1 179 140 Bl shows chambers, where in the top (first longitudinal positions) and the bottom (second longitudoinal positions) of the chamber a part of the inner wall of said chamber is parallel to the central axis: thus there where the piston rod is positioned when the pump is either not in use or where the piston rod is changing its direction, the last mentioned which also occurs in the top of the chamber, by a user, when the pump is in use. No reasoning was disclosed for the parallellity in EP 1 179 140 Bl

For said piston type to move from second to first longitudinal positions in said chamber is possible when said piston is engagingly movable or when said piston is sealingly movable in said chamber.

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

said chamber has an exit between a convex wall and concave wall,

said exit is communicating with a hose.

The longitudinal cross-sectional sections may have convex and/or concave sides. The part of the chamber where convex shapes end and where a concave wall part may begin, and which may matching a cone shaped bottom part, is used in a bicyle floor pump for the purpose to keep the convex /concave shaped part of the chamner on a certain ergonomical height, so that pumping is comfortable for the user (WO/2008/025391).

If said bottom part is hollow, it may be used it in tree ways. An option is to keep this part open, and add an exit to said chamber at its second longitudinal position. Said exit may preferably communicate directly with a hose.

Optionally said exit comprises a check valve, where said check valve is communicating with an expansion chamber, which is built in the bottom part of said chamber. The problem is, that such expansion chamber may be only nessessary for higher pressures, and is than delaying the speed of the pump at lower pressures, because the volume of said expansion chamber- is to be inflated - as well, irrespectively the pressure. Such a solution may be nessesary if a piston would jam in a concave shaped transition from convex shaped wall parts to a further longitudinal position of the chamber, or the piston would be too big to travel to a further longitudinal position.

In the third aspect, the invention relates to a combination of a piston and a chamber, wherein: said concave shaped inner walls are positioned at least between two common borders.

Preferably may said hollow part be used as an additional pumping volume of said chamber , and the piston should be able to move toward and in said bottom part without jamming. Necessary is than a smooth transition from convex shaped wall of cross-sectional sections, said transition comprising a concave shaped wall. Depending on the heigth of the cross- sectional sections - thus the pressure rate - these concave shaped walls may be positioned at least between more than two common borders, the last mentioned at high pressures.

If there is not enough space near a second longitudinal position for the piston to move, one can chose to use that, there must be enough space to have the piston at that position and allowing it to move,

In the third aspect, the invention relates to a combination of a piston and a chamber, wherein: said second chamber comprising a third chamber, communicating

through a check valve with said second chamber

Thus, there may be a point on the wall of said chamber where counted from a first longitudinal position, the convex shape of the sides of the longitudinal cross-sectional area's have to transfer to that part of the chamber in the bottom, where the wall of the chamber wall is parallel to the central axis. In order to do that smoothly, the transition needs to be from convex to concave - thus the shape of a side of the longitudinal cross-section at the transition needs to be concave in the direction from a first to a second longitudinal position.

If the piston has a sealing which takes a certain longitudinale length, so much that the sealing cannot comply to the transition from convex shaped sides of the longitidinal cross-section to a concave shape, then a solution may be to close the chamber there and create an exit by a non-return valve, and use the rest of the chamber as an expansion vessel. This may be usefull for a proper pumping at high pressures.

The positions of said common borders are in both cases (the bottom part used as additional pumping space vs. used as expansion vessel) on different lengths from a first, longitudinal position, while their in-between distances are different - the stroke volume of a pump with an expansion vessel is less that that of a pump which is using the bottom part as part of the stroke volume. In a fourth aspect, the invention relates to to a combination of a piston and a chamber, wherein:

Said chamber is elivated by a fourth chamber which is open, said chamber has an exit, which end in said fourth chamber. The fourth chamber is just the basic chamber with its chacteristic shape, and nothing more. Said chamber may have an exit which is a nippel.

In a fifth aspect, the invention relates to a combination of a piston and a chamber, wherein: said exit is communicating with a hose,

In order to optimize the pumping speed, the hose of a bicycle pump may be expandable upon a certain pressure, so that an expansion vessel is created there. That means that the pump is pumping very efficiently at low pressures, where the hose is not creating an expansion vessel - such a pressure vessel creates more volume to the volume of the tyre alone, to be pumped. Most of the pumping is done for low pressure tyres. The expansion of the hose may be limited by a reinforcement of the hose, and the expansion may be done only on a part of the hose.

The piston may be engagingly movable relative to said chamber wall.

The piston may be scalingly movable relative to said chamber wall

19616 - added matter to the description of 19620 in 19627

Using the chamber from Fig. 21 A, which is used in an advanced bicycle pump, the amount of energy used may be reduced by approx. 65% at 8-10 Bars pressure, in relation to current high pressure bicycle pumps. This has been calculated as follows:

The chamber of Fig. 21 A has been designed, so that max. force is 260 N, at any pressure, specifically the higher pressures, thus also at 8 or 10 Bars.

Current high pressure pumps are comprising a straight cylinder with an internal diameter of ø 27 mm, so that the working force at 8 Bar is: F = p x O = 0,8 x 0,25 x 3,14 x 27² = 458 N. At 10 Bar this is: 572 N

The reduction at 8 Bar is: 458-260/458 = 198/458, so that the reduction is: 43%, and at 10 Bar: 54%. At 12 Bar: 687-272*/687 results in 60%, while 14 Bar gives: 801-318**/801= 66% and 16 Bar: 916-363"7916 = 60,3%.

The efficiency of said advanced bicycle pump is much higher than the current high pressure bicycle pumps, and that has influenced the choice of the 260N as a maximum force. However, the design has been made that the pump may have a higher pressure rate than 10 Bar, when the ø 17mm straight cylinder part is being used as well, besides the conical part of the chamber: F at 12 Bar: 1,2 x 0,25 x 3,14 x 17² = 272N*; F at 14 Bar: 318N**, 16 bar. 363N***.

Conclusion: the stated 65% at 8-10 Bar should have been 54% - however, as the chosen maximum force of F = 260N influences the result, it may be a good to recalculate the chamber which as optimized for a bicycle pump, but now specifcially for the use in a motor.

19617 - added matter for 19620 elongate conical chamber design in 19627

The chambers of Figs. 21A.21B, 22-25 (incl.) of EP Patent Application No. 100754027 (08-09- 2010) have been designed, based on the following mathematical considerations.

The shape of an elongate conical chamber of a pump, having a centre axis, is a line connecting certain dots (x-coordinate: along said centre axis, y-coordinate: perpendicular on said centre axis) outside said centre axis. Said chamber having different cross-sectional area's, and a first and a second longitudinal position, the first longitudinal position having a bigger cross-sectional area than that of a second longitudinal position, wherein between a piston is moving, said piston is sealingly connected to the wall of said chamber, having a production size corresponding with the circumference of said second longitudinal position, said piston having a certain pre-determined maximum working force due to said shape of teh chamber. The position of said dots relative to said centre axis is determined as follows.

When said piston is moving in an elongate conical chamber, from said first to said second longitudinal position, is the rest volume V_x , which is defined as the volume of said chamber at a position L_x , L_x measured from the overpressure side of said piston to e.g. a farthest away second longitudinal position (0-point), where there is an overpressure P_x , the overpressure P_x is counted in relation to a standard pressure, e.g. the atmospheric pressure, used in this calculation:

V_x = 3,14.[0,00046. S_x ³ +(1 ,118-0,00139.L). S_x ² + (900-2,236.L + 0,00139.L²).S_X] where:

V_x is the rest volume at P_x= z Bar over standard pressure, where V_x = V₀ / (z+1).

Vo = is the total volume of said conical chamber, where S = L = the total length of said conical chamber.

S_x = a step in the iterative calculation process. The longitudinal positions where P_x = z Bar (z ) occurs within a certain predefined pressure window (e.g. 1 - 10 Bar overpressure), can now be calculated iteratively (in order to overcome calculations of 3^rd degree equations, when no computer software is available), with the step S, which may be a part (e.g. 1/1000) of the total length L of said conical chamber, counted along said centre axis: The S_x is found from said equation, and gives the x-coordinate of said dot, as S_X.L. If said chamber is comprising non-conical parts (as can be seen in e.g. Figs.21A,B), than only the projected length of conical wall parts on said centre axis need to be used in the calculation of L and Lx. The y-coordinate of said dot is found as follows.

If a certain maximum working force F_max has been chosen, than the position of said dots at a certain longitudinal position Lx at the centre axis, from a chosen 0-point, can be derived as follows:

Dx = F_max / 0,008 . Ρχ (P_x in Bar, D in mm, F in kgf)

The y-coordinate of said dot from said centre axis at said longitudinal position S_X.L is D_x/2, if a symmetrical chamber design in the transversal direction has been chosen, as is in said Figures.

The shape of the chamber wall is than a line through all the points found. In practise is it possible to smoothen ('peditise') said line, if it is drawn as a polyline, so that a contineous shape of a chamber wall results.

19622 a deformable fluid

The use of fluid within the actuator piston may be as follows:

1. a gaseous medium, such as air or N₂: preferably for the CT pressure management system,

2. a combination of a gaseous and a liquid, 3. a liquid, which may be hydraulic oil or H₂0: preferably for the ESVT pressure management

system.

The use of a liquid may give a better economy for the pressurazation of the actuator piston, as by moving a volume of liquid to and from the actuator piston by the pump, no or only a bit heat and cold, resp. may be generated - contrary the (de)pressuration of a gaseous medium.

And, the reduction of the pressure of a gaseous medium, which takes heat, may result in icing of the wall of the actuator piston. This will affect also the lubrication of said actuator piston with the wall of the chamber, thus may affect the efficiency.

Because a liquid cannot be compressed, may the increase of the pressure taking place at the very last part of the traject of the piston of the pump. This works fine with a quickly rotating camshaft or crankshaft, as shown in e.g. Fig. 90L.

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

19630 circular chamber design SUMMARY OF THE INVENTION

The circular chamber shown in Fig.BC and 14D, where a chamber may be moving and the piston(s) do(es) non-moving, has been updivided into e.g. four identical sub-chambers. These chambers have been constructed in such a way that that the effect of each may be that the circular force of each piston, having a different position in each of the circular sub-chambers, on the chamber wall may be identical. This, to avoid unnecessary friction, which would decrease efficiency, and add to wear of the pistons. The chamber may have a constant circular force, thus a constant torque. The size may only be depending on the pressure.

As such is it not necessary to updivide a circular chamber into more than one chambers, in order to comprise more than one piston. However, the angle of the wall of said sub- chambers is bigger than that of one chamber, having the same circle as centre axis. Thus the force of each chamber is bigger, than if onely one chamber was used for several pistons.

The chamber shown in Fig. 12B, where the piston may be moving and the chamber may not, may have in fact the same basic design as the one mentioned above for Figs. 13C and 14D. The piston may have a constant circular force on said chamber wall.

Said sub-chambers have been constructed, so that the chamber is comprising two circle sections in the circular section. Each of the circle sections have its own centerpoint, which are lying in opposite quadrants, around and at an identical distance of the center point of the circular centre axis of the (sub)chamber. Said circle sections are lying around a centre axis of the chamber, which may be a circle.

SM - PVT1

In a final version, we expect a cross-sectional section of such a chamber, in comparison with that of the elongate chamber of Figs. 21A/B where there are (virtual) common border lines (9,11,13,15,17,19,21,23,25,27) parallel to each other and perpendicular to the centre axis (3) of said elongate chamber (1), that a common border line in a longitudinal cross-section of the circular chamber is converging with a line drawn from the farthest boundary of said chamber in the cross-section to the centre point of the centre axis of said circular chamber (e.g. the two arrowed lines in Fig.27C with two center points) - but not is known where the exact centre point is, and whether or not the centre point of the farthest circular chamber line of said cross-section is identical with the centre point of the nearest circular chamber line of said cross-section (in Figs. 27A-C we assumed two centre points), in view of the requirement, that the maximum force of the actuator in said chamber on said chamber wall is independent of the position of said actuator in said chamber, and thus independent of the inside pressure of the actuator.

SM - PVT2

A chamber (with the above mentioned characteristics) is engagingly and/or sealingly moving over said sphere shaped piston (Fig; 1 OH with said attempted configuration of the chamber), which is positioned in said chamber. By moving the chamber over said piston a comparable problem arizes, as exists with the front wheels of a car, turning around a corner - both front wheels are not positioned at the same distance to the rotation center(s?), and in order to get the car around the corner, the wheels need to have independent axles, and neither the angles of said wheels in relation to said direction are not the same at the same time, nor the speed of said wheels. Thus, the reaction forces from the chamber on a contact area of the piston are not equally divided over the circumference of said contact line, which should (?) be identical with said common border lines (of an elongate chamber).

Thus, in that case may the engagingly/sealingly connection to the wall of said piston not be a circle line, but more a combination of a circle point (on the boundery of the cross-section nearest to the center of the circular chamber) to a circle section (on the farthest boundery of said cross-section from the center of the circular chamber), and in between said point and section sections of different sizes and possibly also shape(s). This may not be a big hazard, as the connection to the wall of said chamber only needs to be engagingly, in order to generate motion of said chamber. Due to the several sizes of a circumference, said contact may become from sealingly (nearest the centre of the circle round centre axis of said chamber) to engagingly (farthest to from the centre of the circle round centre axis of said chamber), and in between all kinds of combinations of sealingly- and engagingly contacts. This affects the size of the friction between the piston and the chamber wall, and thus the direction in which the relative motion may be generated - in this assumed configuration should said direction be that of the shape of the chamber - is it in our attempted configuration (Figs 27A-C).

In order to reduce the friction may the sphere piston be rotatable around its piston rod - thus around the centre axis of the piston rod, which may be parallel to an axis through a centre point of said chamber, perpendicular the cross-sectional section of said chamber. ACTUATOR PISTON AND CHAMBER GEOMETRY

Configurations of piston and piston chambers are considered: Circular conic tubes containing a constant area, variable volume, flexible actuator, piston with wall contact. Chambers are constructed

as Fermi tubes. Explicit calculations of volumes and contact areas

are appended in a roughly commented Maple worksheet. The actuator force distribution is indicated. Figures are somewhat extreme

- for the sake of illustrating the importance of the geometry.

1. Fermi tube construction

The central base circle (around which the chamber is 'bent') is parametrized by 'unit speed', has radius R and center at the origin (0, 0, 0) in a fixed (x, y, ^-coordinate system. See blue circle in figures Z^Jk etc. The vector function for the base circle is standard: ^ H

(1.1) j{u) = R · (cos(u/R), sin(u/R), 0) .

Along this base circle we will consider only the turning angle interval u E [0, L] for which the piston has contact with the chamber wall.

In each orthogonal plane (see figures 1 and 2) to the base circle for u 6 [0, L] we define a circle, which will eventually trace out the full chamber and thence also that part of the piston which has chamber- wall contact. These circles have radii p(u) which depend on the base circle parameter u 6 [0, 1/]; and they all have their respective centers on the base circle.

The family of circles trace out a tube surface, a so-called Fermi tube, around the base circle.

We will assume that the function p(u) is linear in u so that the corresponding Fermi surface may be called conic, see corresponding figures <6, 7_¾ and 8. The conic effect (which will eventually drive the piston inside the chamber) can be obtained by any other increasing function of u. The linear radial function is then the following (this is applied for specific values of and β in the Maple appendix and used for illustrations in this report): 2 PISTON AND CHAMBER

(1.2) p(u) = ^■ u + β

The parametrized Fermi tube surface with radius function p[u) which is 'bent' around the base circle is then given by the vector function:

(1.3) r(u, v) = (u) + p(u)^■ (cos(u) · ei(w) + sm(v) · e₂(u)) , where e_\(u) and e₂{u) are orthogonal unit vectors which span the orthogonal plane to the base circle as shown in figure 1:

ei(u) = (cos(u/R), sm(u/R), 0)

(1.4)

e₂(u) = (0, 0, 1) .

The parametrized Fermi tube solid with radius function p(u) which is likewise 'bent' around the base circle is then:

(1.5) + sin(u) · e₂(tt))

Note that the surface is obtained from the corresponding solid simply by setting w = 1 :

(1.6) r(u, v) = r(u, v, 1) .

The volume of the Fermi tube solid (corresponding to the turning angle interval [0, L\) is determined by

(1.7) Vol = w) du dv dw ,

where the Jacobi function integrand is given by the partial derivatives of r as follows:

(1.8) J(u, v, w) = \(r_u ^f x r_v' r_w' \ .

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

(1.9) Area = / / J(u, v) du dv ,

J J u=0

where now the Jacobi function integrand is:

The Maple output appendix contains an example of the calculation of the respective total area and total volume calculated from the chosen values of the constants defining the geometry in the particular case considered and shown. This is fully general and can be numerically evaluated with any other choice of geometric descriptor values.

The total area and total volume includes the values from the end caps which we now discuss. PISTON AND CHAMBER 3

2. THE END CAPS

We assume that the end caps are spherical. This is not absolutely needed. What we need is a circular fit to the tube part of the chamber in both ends and a handle on the enclosed volume and total surface area of the piston. Both are obtained most easily - for the present model considerations - by spherical end caps, see figures A and 8?

In fact the sperical assumption is not completely realistic either:

Given a perfectly elastic piston material it will at all times have constant mean curvature wherever it has no wall contact, i.e. in this setting it will (tend to) have the same spherical radius at both ends. This condition is not implemented in the present discussion.

With a physically precise description of the flexible piston material it is possible to estimate the actual shape of the end caps, the volume they enclose, and thence at each instance of time the internal pressure inside the piston.

Spherical caps have simple geometric expressions for their area and 'enclosed' volume, i.e. the volume cut off from a solid sphere when cutting off the cap by a planar cut. Here we will therefore continue with this Ansatz of spherical caps.

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

(2.1) A{h, p) = · (a² + h²) .

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

(2.2) V(h, p) = - h - (3a² + h²) .

6

For completeness we display also the radius of the virtual sphere from which the respective end caps are taken for u = 0 and u = L respectively:

(2.3) r(u) = p(u) - /l + (p>(u))² .

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

^(2'4) = p(u) ( 1 + {fS{u)Y - p'{u)) .

Thus the end cap areas and volumes are determined solely by the respective values of p and p' when the spherical Ansatz is assumed to 4 PISTON AND CHAMBER

hold.

Since the end cap(s) are supported or attached to a shaft, say a rigid version of the base circle, this attachment and the induced coupling of forces there between shaft and piston will alter the spherical geometry of the piston end(s). Given a precise description of the attachment and of the piston material it could be possible to estimate the geometry of the resulting deformed end caps. This will not be considered here.

3. MOVING THE PISTON AND SHAFT ATTACHMENT

Most important is the area and the geometry of the precise contact between the piston and the chamber wall. It is via this contact that the driving force on the piston is activated. In the present model the wall contact is modeled by a Fermi tube around a given base circle; volume (pressure) and area (forces at the wall) are calculated accordingly.

The actual sliding force along the wall of the chamber is obtained by geometrically symmetric (around that direction as axis) double projection of the gray total force on the chamber segment shown in figuresg₎ 0₎ to, 11, 12, and 13 be ew. Hence the resulting sliding force is proportional to the longitudinal length of the segment and to the internal pressure of the piston; pressure = force per area.

Depending on the friction model (friction between chamber wall and piston) and depending on the material properties (elasticity etc) of the piston, this resulting force will drive the segment in the longitudinal direction. Since the force at each segment is proportional to the longitudinal length of the segment and hence proportional to the distance of the segment from the center of the base circle, it will tend to (to first order and again very much depending on the physical descriptors alluded to above) orchestrate the resulting motion of the free piston surface as a rotation around the center of the base circle.

If the piston is attached to a shaft along the base circle in the chamber, the force described can likewise be applied to pull or push the attached circular shaft into circular motion around the center of the base circle. 19640 SUMMARY OF THE INVENTION

EP 1179140B1 shows on Figs. 5A-5H (inch) a piston (Figs. 105A-105H of this patent application), which is comprising six support means 43, which are rotatably fastened around an axle 44 to a piston rod 45. The other ends of said support means are assembled on an impervious flexible sheet, positioned between a flexible O-ring, which is sealingly connected to the wall of a piston-chamber combination, where the chamber is conical. Said O-ring is squeezed to the wall by said support means, due to pulling springs which at one side have been assembled on said piston rod, and at the other end on said support means near said O-ring, so as to spread said support means from the piston rod to the wall of the chamber. Additionally a spiral spring, which is circleround laid on the impervious sheet, having its center on the centre axis of said chamber, and pressing said O-ring to the wall of said chamber, there where said support means are not supporting directly said O-ring. This was a main solution as a solution principle.

The not yet solved aspect of this construction is that said impervious flexible sheet is free hanging and it may be pushed inwards (change shape) the piston (Fig. 5G, 5H) when pressurized by a fluid under said sheet. Another not yet fully developed aspect is a proper assembling of the O-ring to said support means. And, a proper assembling of said support means to a means which is keeping the O-ring in place between the assembling points of said support means to said O-ring.

There may be two preferred solutions for avoiding the change of shape of the impervious flexible sheet. Other solutions may be possible, but have not been not shown.

One is that said impervious flexible sheet may be assembled at the end of the piston rod, e.g. by a screw. Another solution may be, just to vulcanize said sheet on and around the piston rod. This fastening of said sheet to the piston rod may substantially reduce (but bot avoid) the change of shape of said sheet, when pressurized. And, additionally, a shape change of said sheet may additionally be reduced by a proper reinforcement of said sheet. First of all, the sheet may need to have a production size having a circumference which is approximately that of the circumference of the chamber wall at a second longitudinal position. In order to seal said sheet to the wall of the chamber, when the piston is moving to a second longitudinal position, said sheet may need in the first instance to be spreaded, when firstly moving the piston from said second longitudinal position to a first longitudinal position. The pulling springs on said support means may be pulling a bit more than the pulling forces in said impervious sheet, pulling it back to its production size, when the piston is not at a second longitudinal position. A third force may be pulling the O-ring from the wall, and that happens when said sheet would bend upwards when pressurized. In order to substantially prevent that, the reinforcement may comprise concentric reinforcements, which may have been made of flexible material in its length, or, if made of non- flexible material as a spiral, having the centre axis of the piston rod as centrum. Other reinforcement possibilities may be possible, but are not shown. The use of said reinforcement patterns mean that the sheet may be widened in 2D, in a transversal plane, perpendicular the centre axis of said chamber, and only a bit in the direction of the centre axis of said chamber.

Preferably is the reinforcement layer of said sheet positioned closest to the high pressure side of said sheet, and another layer without reinforcements may be vulcanized on the first mentioned layer. The production thickness of each layer may be so thick, that the decreased thickness at a first longitudinal position may be enough for a longduring proper functioning of said piston.

Also the O-ring may have a production size where its external circumference is approximately the size of the circumference of said chamber at a second longitudinal position.

Also here should the production diameter of said O-ring be big enough to compensate for the decrease of thickness when the piston has been moved to a first longitudinal position.

The impervious sheet may be vulcanised on / in said O-ring, so as to achieve a proper sealing, when the O-ring is sealingly connected to the wall of the chamber.

The lying spring may be vulcanized on both said O-ring, the ends of said support means and on the impervious sheet. This keep the whole together.

Having assembled the impervious flexible sheet onto the piston rod, the widening of said sheet may substantially be caused by the pulling forces of the springs on said support means, and by the rotation forces of said support means. There may be a balance of forces of the internal pull forces of the impervious flexible sheet , O-ring and the pushing forces of the lying spiral spring and the pushing forces of said support means, and the reaction forces of the wall to the O- ring, so that allways the O-ring may be pressed onto the wall of the chamber for achieving a sealingly connection. The lying spiral spring shown in the Figures of said prior art, which mainly should keep the O-ring in place between the support means ends, would possibly not give enough force to do that job. Instead, an elastic metal rod may keep the O-ring better in place. Both ends of said rod may be sliding between two adjacent support means, while two rods may slide along each other through a support means.

19650 SUMMARY OF THE INVENTION

EP 1 179 140 Bl discloses an elasticallyl deformable means, which has been stiffened by stiff members, which are rotatably fastened to a common member, such as a piston rod, in case a piston may be made of said elastically deformable means. The elastically deformable means may have a tranversal cross-section of that of a trapezium. When moving in the chamber from a first longitidinal position to a second longitudinal position, wherein the wall of said chamber at a second longitudinal position is parallel to the centre axis of said chamber, the trapezium becomes more and more a rectangular. Said stiffereners may rotate to an angle where the stifferers are approx. positioned parallel to said centre axis, when the piston is moving from a first to second longitudinal position.

A foam may expand from a second longitudinal position in a elongate chamber to a bigger shape at a first longitudinal posirtion. But it may be done in a different way than expanding an inflatable container which is comprising a flexible wall, with a production size so that the circumference is approximately the circumference of the wall of the chamber at a second longitudinal position (please see e.g. EP 1 384 004 Bl). When it is moved to a first longitudinal position, and it may need to be engagingly connected to the wall of said chamber, the thickness of the wail of said container may be decreased ("balloon effect").

A motor wherein a pump having a piston engagingly and/or sealingly movable in a chamber, wherein

- in the elastically deformable means is made of Polyurethane-foam,

- the PU-foam is comprising a Polyurethene Memory foam and a Polyurethane foam.

- the Polyurethane foam is comprising a major part is Polyurethane Memory foam, and a minor part Polyurethane foam.

An elastically deformable means may be made of a foam. Specifically good characteristics for harsh circumstances as e.g. a moving piston in a chamber of a pump may be Polyurethan Foam. The growing in size of a foam when moving from a second to a first longitudinal position may be done by enlarging the cells wherein the fluid is positioned, which may be present in said chamber. That may be possible, when the cells are open, that is to say, that the inside of said cells may be communicating with the atmosphere around said foam, in said chamber. Thus the foam at a second longitudinal position needs to be under pressure so as to be able to decrease the size of the open cells in the foam, and, at a second longitudinal position needs the foam be under pressure, in order to be able to expand itself, when moved to a first longitudinal position. The foam, thus the material of the walls of the open cells may than needed being very elastically. Such a material may be a Polyurethane (shortly 'PU') foam, and a very flexible type of PU foam may be the so-called Memory Foam.

Materials which are very flexible may however not withstand very well big pressure by itself, such what a piston needs to be capable of. In order to gain a better resistance to pressure, a kind of a sandwich may be made, which may be made of e.g. a two layer PU, of which one layer is made of less flexible PU foam than PU Memory Foam, and a layer of PU Memory Foam - the two layers may be glued to each other. If there is no space for layers and/or a sandwich may be difficult to be produced, a mixture of a PU foam and a PU Memory Foam may be the solution. The percentage of a normal PU Foam may be a minor part of the total mixture.

A motor wherein said pump having said piston wherein

the support members are bendable,

said support members have been pre-determined bending force,

said members being locked in a holder, which is connected to the piston rod, and being rotatable around said bend of said stiffener in said holder,

said end is being under pressure of an adjustable member,

said longer end of said stiffener having an increased thickness.

Said Memory Foam material is quickly regaining its original size when released, after having been depressed, at normal working temperatures, such as 10° - 100° C. At lower temperatures such as around the freezing point, it takes longer time, and that may be too long, in order to comply to the demand of engagingly and/or sealingly connected to the wall of the chamber. It may be necessary that said stiffeners are being made of a spring material, so that when the piston is moving from a second to a first longitudinal position, said stiffeners may be pressing the foam outwards. A pre-determined bending force may be necesasary, and that may be done by e.g. the end of said stiffener, being bended a much shorter length than the total length of said stiffener, thereby the angle being capable of locking the end of said stiffener in a holder - said holder may be connected to the piston rod. The pre-determined bending force may be obtained by an adjustable member, which presses the short end of said stiffeners - it may be a rotatable member, which can be locked in a certain position.

When moving from a first to a second longitudinal position said foam may be being pressed inward by the wall of said chamber, and said foam may need to be in such a shape, that no lateral forces are present, so that the cast foam, which glues to said stiffeners (which may be preferably made of Polyurethane), has become unstuck, so that its function is lost.

In order to avoid that said stiffeners are becoming instuck another measure is to increase the thickness of the long end of said stiffeners, close to where pressure is obtained from the fluid under the piston in said chamber.

A motor wherein said pump having said piston wherein

- said flexible impervious layer has an unstressed production size with a circumference which is approximately the same as the circumference of the wall of the chamber at a second longitudinal position.

A foam piston with open cells is engaingly connected to the wall of said chamber. In order to make it sealingly connectable to said chamber wall it is necessary to add an impervious layer, such as a nature rubber type. This may need to comply to approximately the same sizes of a circumference as an inflatable container type piston. Thus may need the size of said layer having a circumference of that of the chamber wall at a second longitudinal position, unstressed - thus needs the assembling be around a foam under pressure. When moving from a second to a first longitudinal position, the foam and thus said stiffeners) need to press the layer into the shape (trapez) of the foam when being positioned at a first longitudinal position. When returning to said second longitudinal position, said layer may be shrinking into the approx. rectangular shape of said foam at a second longitudinal position: it needs to be flexible. The impervious layer may need to be able to communicate with the fluid of the non-pressure side of said piston in order to be able the open cells to communicate ('breath'), when moving from second to first longitudinal positions and vice versa.

19650-1 improved suspension of foam piston for e.g. pumping purposes

WO2000/070227 discloses a foam piston which has the problem that the foam cannot not properly be mounted on the piston rod, specifically during the return stroke. The reason is that the PU foam cannot be fastened very well to the steel of the piston rod. Another difficulty is the release of the ready piston from the mould, due to the fact that the angles of the several rows of reinforcement pins are increasing outwards from the piston rod side. A further difficulty is that PU foam is not very well fastening on a metal reinforcement pin, even the surface of the last mentioned has been made rough. The improved suspension of the foam piston is the subject matter of this section of the patent application.

The piston disclosed in the section 19650 of this patent application is very robust for professional use. For the use in e.g. a bicycle pump a less robust, still reliable construction may be needed, where also repair may be simply and straight forward.

The solution is according to the characteristic part of the independent claim. The use of metal pins may be maintained, when e.g. the pins have received a surface coating of an appropriate material, e.g. PU when the foam of the piston also is made of PU, before the foam piston has been moulded around said pins - than the pins will fasten enough to the foam, to avoid stripping off the foam of said piston. The metal pins may be made of a steel type which can be magnetized. If the holder plate, to which the pins are designed to transfer the compression force from the high pressure side of the piston to the piston rod, is being magnetized, said pins may be sticking into small holes of about a deepness to said surface, approximately the size of the diameter of said pins. Said holes may have a geometrical design, so that said pins may be able to rotate in said holes. Said pins will be fastened to said holder plate, as soon as these have come near enough to each other, so that the magnetic force can do it's work. Said holder plate may have s small thickness, and may be glued to the piston rod, directly or indirectly on a holder, which is assembled on a piston rod.

Another still more improved version of the pins may be that these have been made e.g. by injection moulding of e.g. PU-plastic, which will stick perfectly to the same type of foam (e.g. PU foam) of the piston. Here is the extra possibility to avoiding stripping the PU foam off the pins, by making many small reduction of the diameters of said pins. The suspension of the pins may be done as follows. The pins may have a sphere shaped end which can be smoothly pressed in a holder plate, having a sphere cavity, so that said sphere end may rotate in said sphere cavity. The pins may have a certain pre-loading, so that the foam will be widened when the piston is moving from a 2" to a 1^st longitudinal position of the chamber, specifically at lower temperatures. This may be done by giving the sphere end of said pins a small lever arm, which is sticking in a plate of flexible material, e.g. rubber. The production angle is than the widest angle of said piston, thus when the piston is at a 1^st longitudinal position of the chamber.

19660 SUMMARY OF THE INVENTION

EP 1 179140 Bl shows an inflatable container piston type, while EP 1 384 004 Bl shows that this piston type should have an unstressed production size wherein its circumference at the second longitudinal position of an elongate chamber, should have a circumference which is approximately the same as the one of the chamber, so as to avoid that the piston is jarriming when moving from a first to a second longitudinal position.

The piston is expanding when moved from a second to a first longitudinal position. EP 1 384 004 Bl shows that a reinforcement for such a desired behaviour may be a layer where the reinforcement strings are laying parallel besides each other in an unstressed production model, and these strings are connecting the two end parts, of which one is mounted on the piston rod, while the other can glide of the piston rod - the rubber is directly vulcanized on both ends. The reinforcement layer is the inner layer, while another, thicker layer than the layer with reinforcement strings, is protecting said reinforcement layer. Both layers are being vulcanized on each other, and at the end parts, there may be another extra layer on top of the two. The function of the second layer is additionally to avoid that the reinforcement strings are 'sticking' out of the outer layer, thereby making a sealingly contact with the wall of the chamber impossible - however, for an engagingly contact is this just fine. Having the second layer on top of the reinforcement layer is working fine in practise, and it has shown be possible to expand near the 330%, e.g. in a chamber of a pump (please see 19620) where the force on the piston rod is constant, from an 017 mm (2^nd longitudinal position) to an ø 59 mm (1^st longitudinal position). With two reinforcement layers on top of each other with a very small angle for overlapping each other, and on top the above mentioned 'second' layer makes the container more strong, but expansions possible are much less 330%.

The types of rubber of the layers rubber may be different, but should be compatible so, that these can be vulcanized on each other, without getting lose from each other under normal working conditions.

It was observed that when the ellipsoide shaped container type piston was expanding completely to its sphere shape, the chance of breaking apart was very present - that is why the design may be changed so that the length of the piston as unstressed production model be increased, by keeping the other variables, such as the chamber design unchanged - thus, the sphere shape may not be reached and neither an expansion to 330%, only an ellipsoide which has almost become the shape of a sphere - this makes the piston reliable, even with one layer with reinforcements.

The shape of the container in an unstressed production state may also be that the wall of the container is not parallel with the centre axis, but parallel to the wall of the chamber because the wall of the chamber at a second longitudinal position is not parallel to the centre axis. Just the wall of the chamber is free of the wall of the container in said unstressed production state.

19660-1.2 Update on the functioning of actuator piston

The actuator piston is comprising a container, said container is comprising a wall around a cavity, said cavity may be inflatable and pressurized by a fluid and/or may comprise a foam, said container is moving from 2^nd to 1^st longitudinal positions of the chamber, when pressurized, in a chamber having cross-sections of different cross-sectional areas and different circumferential lengths at the first and second longitudinal positions, and at least substantially continuously different cross- sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longitudinal position, due to sliding of the wall of said container of said actuator piston on the wall of said chamber.

This may also be the case for chambers having cross-sections of different cross-sectional areas and equal circumferential lengths at the first and second longitudinal positions, and at an intermediate longitudinal position.

Said wall of the piston may preferably having a symmetrical shape in the longitudinal direction of the chamber between the end cabs (the movable and the non-movable), around a transversal central axis, wherein each symmetrical half part having longitudinal cross-sections of different cross- sectional areas and different circumferential lengths at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions between said transversal centre axis and an end cab.

This may also be the case when said circumferential lengths are equal.

Having a reinforcement layer in the wall of said container of actuator piston makes the outside of said wall smooth, and preferably convex shaped, when pressurized from within the cavity of said container. This provides a small contact area with the wall of said chamber. The expansion forces of the wall of said container are directed perpendicular the surface of the wall of said chamber. The expansion forces may be much larger than the pressure inside the cavity of the actuator piston, depending on the t/R ratio (R= transversal radius of a longitudinal cross-sectional section, t = wall thickness of the actuator piston), specifically when t R<«, When said actuator piston is being positioned in a wall of a chamber having an positive angle with the centre axis of said chamber in the direction from a 2^nd to a 1^st longitudinal position, an asymmetry arises in the reaction forces from the wall of said chamber, because there will be no reaction forces on chamber positions nearest a 1^st longitudinal position of the chamber on the ultimate position nearest a 1^st longitudinal position part of the contact area (wall chamber - container), and the consequences are that the wall of said container at these positions will bend towards the wall of said chamber, until the reaction foces of the wall equal the expansion forces of he wall of said container - the wall of said conatiner of the actuator piston is rolling over the wall of said chamber. This rolling is adding to the contact height of the contact area of the wall of said container and the wall of said chamber, where so the frictional forces increase. Said expansion of the wall of container of the actuator piston is causing a small pressure drop inside the wall of said container, when the volume of the enclosed space remaims constant, said pressure drop causes that the expansion forces of the wall of said piston are decreasing, thus also the friction forces. A movement of said actuator piston towards a 1^st longitudinal position may occur (sliding). This may reduce said contact height, because the portion of said wall of the container nearest a 2^nd longitudinal position may reduce its circumference, and thus also that of the contact area nearest a 2^nd longitudinal position. Due to the lubrication between the wall of said chamber and the wall of said container, the propulsion forces are still bigger than said friction forces, and the actuator piston will slide to a new chamber position nearer a first longitudinal position, until said asymmetry of forces occurs again, whereafter the cycle may start again. It is the ability to increase (= rolling) a contact height in a longitudinal cross-section of the engaging wall of the container and the wall of the chamber, thereby making the height in immediate continuation of the existing height larger, that is the main reason of the behaviour of the actuator piston. The means to do so may be for e.g. an ellipsoid shaped actuator piston:

• when present, a bendable reinforcement layer of which the direction of reinforcement is in longitudinal direction approx. parallel to the centre axis of the chamber, • none of almost no reinforcement in the transversal direction,

• preferably a symmetrical wall of the container around a transversal symmetrical axis,

• a smooth surface of the wall of the actuator piston, at least on and continuously until nearby its contact area with the wall of the chamber,

than,

the wall of the container will under internal pressure bend out from an ultimate circumference of the contact area nearest a first longitudinal position, between the wall of the chamber and the wall of the container, and reaching the wall of the chamber, thereby increasing the contact surface area, and

the wall of the container near a second longitudinal position will thereafter under said bending retract from the wall of the chamber,

whereafter the contact surface area between the wall of the container and the wall of the chamber again is decreasing. The actuator piston will stop running towards a I^s longitudinal position, when there may be not sufficient internal pressure to press the wall of the container of the actuator piston towards the wall of the chamber, so that a circumferential leak occurs. This may happen e.g. in case of a chamber shown in section 19620 of this patent application, when the common border of 1 Bar overpressure exists in the chamber - this is earlier in the description disclosed as the "hesitation behaviour".

In practise a behaviour is seen that a container of an actuator piston, of which the movable cab is positioned nearest a 1^st longitudinal position, is moving stepwardsly, when the pressure inside the cavity of the actuator piston is quite low.

The reason may be that the expansion of the wall of said actuator piston, when moving from 2^nd to 1^st longitudinal positions, is additionally forcing the contact area of the wall of said actuator piston to the wall of the chamber nearest to the 1^st longitudinal position, besides the expansion of the wall of the container due to the internal pressure, thus also increasing the friction force.

In case the non-movable cab is positioned nearest a 1^st longitudinal position, thus 'ahead' of the container in the direction of the movement, even the pressure is low, the movement is smoothly.

The reason may be that the extra force of the expansion of the wall of the container may add to the reduced expansion force, and not exceeding the friction force. Thus: the wall of the piston is made of a flexible reinforced material, when pressurized by a pressure source through the enclosed space, which is resulting in a smooth outer surface of said piston wall, and by that, providing a height of the contact area circumferentially in a longitudinal cross-section of said piston, between said piston wall and the wall of the chamber, said height is changing in size during the movement of the piston at intermediate longitudinal positions between the second and first longitudinal positions. This sliding may done over several different contact area's of the wall of said actuator piston, with the wall of said chamber. This is possible, because the wall of said container is convex shaped, flexible, while the several different area's are positioned in continuation of each other.

19660-2 inflatable piston - strength and stiffness

The inflatable piston of the type where an ellipsoi^'de at a 2^nd longitudinal position of a chamber is becoming a enlarged ellipsoi^'de / (almost) sphere, can, regarding strength and stiffness, be compared to a cylindrical vessel with a small wall thickness, which is under internal pressure.

The Hoop stress OH is expanding the wall of the cylinder. The size of said Hoop stress OH IS in general approximately lOx the size of the internal pressure in said cylinder . This is the reason why a the actuator piston already at a low internal pressure is rocketing from a 2^nd to a 1^st longitudinal positions in a cylinder according section 19620 of this patent application.

The size of the Hoop stress 0H depends on the longitudinal position of the piston, the size of the chamber and on the number of reinforcement layers - for one reinforcement layer, and a

- 2^nd longitudinal position / ø 17mm: is approx. 3x the internal pressure in the piston,

- 1^st longitudinal position / ø 58mm: is approx. 3,8x the internal pressure in the piston. The inflatable piston of the type where a sphere at a 2^nd longitudinal position of a chamber is becoming an enlarged sphere, can, regarding strength and stiffness, be compared with a sphere vessel, with a small thickness, which is under internal pressure.

The spherical stress os³ which applies, can be compared with the longitudinal stress OL of a cylindrical cylinder, which is half of the size of the Hoop stress OH . This means that a sphere piston in a circular chamber may give half the propulsion force of that of an ellipsoide. Thus, more than one sphere piston may be available in a circular chamber, in order to reduce the size of a motor, while having a comparable torque.

Thus: the stress which expands the wall of the actuator piston is depending on the thickness t of the wall of the actuator piston, in relation the the transversal radius R of the actuator piston, is C_x = [1-t/R] times the pressure in the actuator piston. Cx may be different form one longitudinal pisition of the actuator piston to another, as R may depend on the transversal radius of the chamber. This may be saving energy, and how much is depending on the slope of the wall of the

¹ σ_Η = pR/t p= internal pressure, R= ½ diameter of the cylinder, t= wall thickness of the cylinder.

² Strength and Stiffness of Engineering Systems, Frederick A Leckie, Dominique J. Dalbello, Springer, 2009

ISBN: 978-0-337-49473-9

³ Os = pR/2t p= internal pressure, R= ½ diameter of the sphere, t= wall thickness of the sphere. chamber, because the propulsion force of an actuator piston is the expansion force of the wall of the actuator x the sin of the angle between the wall of the chamber with its longitudinal centre axis. The bigger said angle is the bigger is the propulsion force. As an example: we find out the magnitude of a motor, as a replacement for a petrol motor for a Golf MK II, which has 081 mm cylinders, stroke length 77,4 mm, and which is operating between 9-10 Bar.

The slope of the chamber is chosen: a = 10°, thus sin 10° = 0,174, while we keep a cylinder 0 = 81mm, at a 1^st longitudinal position - this gives 0 53,7mm at a 2^nd longitudinal position, and a wall thickness of the actuator piston: 3.5mm - pressure at a 2^nd LP = 10 Bar, at a 1^st LP = 2,25 Bar. d = R/t [l - t/R ] = 10,6→ a_m = 24 N/mm² -> F propulsion 1 ⁼ 2125 N

C₂ = R/t [1 - t/R ] = 6,7 → σ_Ηι = 67 N/mm² →· F propulsion 2 = 3933 N

Conclusion: it is possible to use a motor according to this invention, which has approximately the size of a current petrol motor.

19680-2 - Pump Piston comprising a container

The aim of this section is to develop a container type piston, which may be used in a pump, while using the principle disclosed of WO2002/077457, where the circumference of said piston is having a production size of that of the circumference of the 2^nd longitudinal position. That means that an inflatable container type piston is to be inflated from a 2^nd longitudinal position for moving to a 1st longitudinal position and back without jamming. However, it is the experience that the travel: rolling - sliding - rolling etc. from a 2^nd to a 1^st longitudinal position is done solely by means of the internal pressure of said piston, having a continuous outside wall of said piston, a contact area with the wall of said chamber which is positioned under the transversal centre line of said piston, and a movable cab closest to the 1 ^st longitudinal position, while the non-movable cab is closest to the 2^nd longitudinal position.

The experience is that the self propelling ability is out of function, when the wall of said chamber is parallel to the centre axis of said chamber. Thus, in order to use the piston in a pump, the selfpropelling motion should the "rolling" of the wall of said piston over the wall of the chamber should be avoided. This may be done by discontinuation of the outside wall of said piston.

The creation of a self-propelling actuator piston, a "rolling-sliding-rolling etc. of the wall of said piston over the wall of said conical chamber" should be avoided, as it generates a propulsion force in the opposite direction of the pumping force. In order to do so, the contact area between the wall of said chamber and the wall of said piston may be restricted ("dis continuous") to a certain area of the wall of said piston, and that may be done at least in two ways: · the contact area may be a separate part of the wall of said piston - it may expand more that the rest of the wall of said piston,

• the part of said piston closest to the second longitudinal position may have a smaller circumference of a transversal cross-section than that of said contact area. The Hoop stress in the wall of a inflatable container type piston (please see sections 19660, 207 and 653 of this patent application) is causing the expansion of the circumference of said wall, and is the source of the actuator piston to become self-propelling by internal overpressure.

Thus has said Hoop stress a big impact on the sealing ability of said piston to a chamber wall, and thus at the same time is the ability to jam big, when said piston is pushed from a 1^st to a 2^nd longitudinal position. Due to the specific R/t ratio (big radius in comparison to a small wall thickness (which is the layer which is having the reinforcement layer(s)), is the Hoop stress much higher than the pressure inside. A first thought may be that "thus" may the pressure of the gaseous medium inside said piston be low, in relation to the pressure of a medium in the chamber, wherein said piston is situated, and which is compressed by said piston. However, the piston has to seal at any pressure of the medium to be pumped.

As at the same time, it has shown to be impossible to push by hand an inflated (with a compressible medium such as N₂) piston (according those shown in said sections), in a chamber shown in section 19597 of this patent application, said piston is comprising a compressible medium having 1-1 ½ bar (absolute) overpressure (over atmospheric pressure) at a first longitudinal position, from said first longitudinal position to a second longitudinal position, said medium to expand the wall of said piston may preferably be: different from that of a compressible medium such as a gas - e.g. a foam would than be better, even it may contain a fluid in its holes, when the foam having an open structure - it would be preferable that the foam has an open structure - said foam should preferably be at atmospheric pressure at a first longitudinal position, optionally at a low over pressure (e.g. 1 Bar). The foam, and preferably not said medium should be expanding the wall of said piston, optionally may there be a combination of said two factors, and/or different from a medium which is compressible, such as a non-compressible medium (e.g. a liquid such as water),

and communicating with an enclosed space, e.g. a hollow piston rod, in which the medium, which will be pressed out of said foam, thus from said container, when said foam is compressed by the wall of said piston, when said piston is moving from a first to a second longitudinal position, to said enclosed space (e.g. WO2010/094317 or sections 207 and/or 653), in order to avoid a steep rise of the internal pressure, and thereby a possible jamming.

An alternative solution for avoiding the creating a self-propelling actuator piston, when using an inflatable piston, is that the piston may have a wall without of with a reinforced part, whereby said the reinforcement may be minimal, only avoiding any exorbitant swallowing up of the wall of the piston when inflated, and a foam, preferably an open cell foam. The open cells may be containing a fluid, preferably a gaseous medium, optionally a liquid or a combination of a liquid and a gaseous medium. Said foam may be inserted into the piston when the piston is in its first longitudinal position, and the wall of said piston is engagingly and/or sealingly connected to the wall of the chamber, so that it is filling up the biggest volume of said piston, when the wall of said piston is in tension, with a smaller wall thickness than that when produced (in the second longitudinal position). The foam may be able to be compressible to an high order (e.g. 5:1 when using the piston of sections 19660 and /or 19680), so that the piston may be filled with a denser foam when being at a second longitudinal position, where almost all of the open cells have been closed - when moving from a first to a second longitudinal position the medium inside said foam may then be removed from said piston, e.g. to a piston rod. In order to avoid the building up of high pressure inside said piston rod, may the piston rod have a movable piston, which is reducing the volume of the medium in the open cells (when not being at a second longitudinal position). This high pressure would be causing of the piston becoming an actuator piston, and jamming when moving from a first to a second longitudinal position. The result may be a piston which is changing size (and may additionally be changing shape), with just a sufficient sealing force to the wall of the chamber during the pump stroke, without moving itself, and without jamming The wall of said piston made of a flexible material, e.g. rubber, makes said piston a reliable piston for a pump.

The production of said container piston comprising a foam would be as follows: the wall of said container piston is produced when it is at a 2^nd longitudinal position. Thereafter a fluid is injected into the cavity of said container, when it is at a 1^st longitudinal position - the movable cab is moving towards the other cab, and the wall of the container is bowed. Then the position of the movable cap is being fixed, whereafter the fluid is released from the cavity. The foam blend is now injected, and the cavity of said contianer is closed. After hardening, is the fixture of the movable cap removed. Then a shrinkage may occur of the wall of said container, due to the nature of said foam, comprising open cells. This shrinkage may be compensated by a very small increasing of the pressure of the medium in said open cells, or by having another cavity within a impervious flexible wall, positioned within the center of said foam, said cavity may be inflated, and which then presses the foam towards the wall of said container piston, in order to get the wall to its originally planned position.

The separate wall part of a piston is 'sticking out' of the wall of the piston - it has thereby a bigger circumference that the rest of the wall nearby, while the transition of circumferences from the wall of said piston to the separate part is more or less abruptly or stepped.

The contact area of said separate part with the wall of said chamber may be small - this may be done by choosing the right shape of the separate part, e.g. circle segment, wherein the top of said segment is having contact with the wall of the chamber.

207 SUMMARY OF THE INVENTION

In general, a new design for a combination of a chamber and a piston for e.g. a pump must ensure that the force to be applied to operate the pump during the entire pumping operation is low enough to be felt as being comfortable by the user, that the length of a stroke is suitable, especially for women and teenagers, that the pumping time is not prolonged, and that the pump has a niinimum of components reliable and almost free of maintenance time.

In a first aspect, 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 area thereof and, at a second longitudinal position thereof, a second cross-sectional area, the second cross-sectional area being 95% or less of the first cross-sectional area, the change in cross-section 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.

In the present context, the cross-sections are preferably taken perpendicularly to the longitudinal axis.

Also, due to the fact that in order for the piston to be able to seal against the inner wall of the chamber during movement between the first and second longitudinal positions, the variation of the cross- section of the chamber is preferably at least substantially continuous - that is, without abrupt changes in a longitudinal cross section of the inner wall.

In the present context, the cross-sectional area of the chamber is the cross-sectional area of the inner space thereof in the cross-section selected.

Thus, as will become clear in the following, the fact that the area of the inner chamber changes brings about the possibility of actually tailoring the combination to a number of situations.

In a preferred embodiment, the combination is used as a pump, whereby the movement of the piston will compress air and output this through a valve into e.g. a tyre. The area of the piston and the pressure on the other side of the valve will determine the force required in order to provide a flow of air through the valve. Thus, an adaptation of the force required may take place. Also, the volume of air provided will depend on the area of the piston. However, in order to compress the air, the first translation of the piston will be relatively easy (the pressure is relatively low), whereby this may be performed with a large area. Thus, totally, a larger amount of air may be provided at a given pressure during a single stroke of a certain length.

Naturally, the actual reduction of the area may depend on the intended use of the combination as well as the force in question.

Preferably, the second cross-sectional area is 95-15%, 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. A number of different technologies may be used in order to realise this combination. These technologies are described further in relation to the subsequent aspects of the invention.

One such technology is one wherein the piston comprises:

a plurality of at least substantially stiff support members rotatably fastened to a common member,

- elastically deformable means, supported by the supporting members, for sealing against an inner wall of the chamber, the support members being rotatable between 10° and 40° relative to the longitudinal axis. In that situation, the common member may be attached to a handle for use by an operator, and wherein the support members extend, in the chamber, in a direction relatively away from the handle.

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

Also, the combination may further comprise means for biasing the support members against an inner wall of the chamber

Another technology is one wherein the piston comprises an elastically deformable container comprising a deformable material. In that situation, the deformable material may be a fluid or a mixture of fluids, such as water, steam, and/or gas, or a foam.

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

Then, at least part of the deformable material may be compressible and wherein the first shape has an area being larger than an area of the second shape.

Alternatively, the deformable material may be at least substantially incompressible

The piston may comprise an enclosed space communicating with the deformable container, the enclosed space having a variable volume. The volume may be varied by an operator, and it may comprise a spring-biased piston.

Yet another technology is one , wherein the first cross-sectional shape is 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.

In that situation, the first cross-sectional area may be 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% larger than the second cross- sectional area.

Also, the first cross-sectional shape may be 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.

In addition, the first cross-sectional shape may be at least substantially circular and wherein the second cross-sectional shape comprises two or more at least substantially elongate, such as lobe-shaped, parts.

Also, in the cross-section at the first longitudinal position, a first circumference of the chamber may be 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. Preferably, the first and second circumferences are at least substantially identical. An optional or additional technology is one wherein the piston comprises:

an elastically deformable material 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, and

- a coiled flat spring having a central axis at least substantially along the longitudinal axis, the spring being positioned adjacently to the elastically deformable material so as to support the elastically deformable material in the longitudinal direction.

In that situation, the piston may further comprise a number of flat supporting means positioned between the elastically deformable material and the spring, the supporting means being rotatable along an interface between the spring and the elastically deformable material.

The supporting means may be adapted to rotate from a first position to a second position where, in the first position, an outer boundary thereof may be comprised within the first cross-sectional area and where, in the second position, an outer boundary thereof may be comprised within the second cross-sectional area.

In a second aspect, 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 area thereof and, at a second longitudinal position thereof, 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, 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, the piston comprising: a plurality of at least substantially stiff support members rotatably fastened to a common member,

elastically deformable means, supported by the supporting members, for sealing against an inner wall of the chamber the support members being rotatable between 10° and 40° relative to the longitudinal axis.

Thus, the manner in which the piston is able to adapt to different areas and/or shapes is one wherein the piston comprises a number of rotatably fastened means holding a sealing means. One preferred embodiment is one wherein the piston has the overall shape of an umbrella.

Preferably, the common member is attached to a handle for use by an operator, such as when the combination is used as a pump, and wherein the support members extend, in the chamber, in a direction relatively away from the handle. This has the advantage that increasing the pressure by forcing the handle into the chamber, will simply force the supporting means and the sealing means against the wall of the chamber - thus increasing the sealing.

In order to ensure sealing also after a stroke, the combination preferably comprises means for biasing the support members against an inner wall of the chamber.

In a third aspect, 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 area thereof and, at a second longitudinal position thereof, 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, 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 the piston comprising an elastically deformable container comprising a deformable material.

Thus, by providing an elastically deformable container, changes in area and/or shape may be provided. Naturally, this container should be sufficiently fastened to the piston in order for it to follow the remainder of the piston when the piston is moved in the chamber. The deformable material may be a fluid or a mixture of fluids, such as water, steam, and/or gas, or foam. This material, or a part thereof, may be compressible, such as gas or a mixture of water and gas, or it may be at least substantially incompressible.

When the cross-sectional area changes, the volume of the container may change. Thus, in a cross-section through the longitudinal direction, the container may have a first shape at the first longitudinal direction and a second shape at the second longitudinal direction, the first shape being different from the second shape. In one situation, at least part of the deformable material is compressible and the first shape has an area being larger than an area of the second shape. In that situation, the overall volume of the container changes, whereby the fluid should be compressible. Alternatively or optionally, piston may comprise a second enclosed space communicating with the deformable container, the enclosed space having a variable volume. In that manner, that enclosed space may take up fluid when the deformable container changes volume. The volume of the second container may be varied by an operator. In that manner, the overall pressure or maximum/minimum pressure of the container may be altered. Also, the second enclosed space may comprise a spring-biased piston.

It may be preferred to provide means for defining the volume of the enclosed space so that a pressure of fluid in the enclosed space relates to a pressure of fluid between the piston and the second longitudinal position of the container. In this manner, the pressure of the deformable container may be varied in order to obtain a suitable sealing.

A simple manner would be to have the defining means adapted to define the pressure in the enclosed space at least substantially identical to the pressure between the piston and the second longitudinal position of the container. 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).

In fact, the use of this piston may define any relation between the pressures in that the enclosed space in which the piston translates may taper in the same manner as the main chamber of the combination.

In order to withstand both the friction against the chamber wall and the shape/dimension changes, the container may comprise an elastically deformable -material comprising enforcement means, such as a fibre enforcement.

In order to achieve and maintain a appropriate sealing between the container and the chamber wall, it is preferred that an internal pressure, such as a pressure generated by a fluid in the container, is higher than the highest pressure of the surrounding atmosphere during translation of the piston from the first longitudinal position to the second longitudinal position or vice versa.

In yet another aspect, 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,

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.

In the present context, 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.

Preferably, the first cross-sectional area is at least 5%, preferably at least 10%, such as at least 20%, preferably at least 30%, such as at least 40%, preferably at least 50%, such as at least 60%, preferably at least 70%, such as at least 80, such as at least 90% larger than the second cross-sectional area.

In a preferred embodiment, the first cross-sectional shape is at least substantially circular 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.

In another preferred embodiment, 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.

When, in the cross-section at the first longitudinal position, 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, a number of advantages are seen. 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. Preferably, 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.

Alternatively, 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:

elastically deformable means, supported by the supporting members, for sealing against an inner wall of the chamber.

Another type of piston is the one comprising an elastically deformable container comprising a deformable material. Another aspect of 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 area thereof and, at a second longitudinal position thereof, 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, the piston comprising: an elastically deformable material 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, and

This embodiment solves the potential problem of merely providing a large mass of a resilient material as a piston. The fact that the material is resilient will provide the problem of deformation of the piston and, if the pressure increases, lack of sealing due to the resiliency of the material. This is especially a problem if the dimension changes required are large. In the present aspect, the resilient material is supported by a helical flat spring. A helical spring is able to be expanded and compressed in order to follow the area of the chamber while the flat structure of the material of the spring will ensure that the spring is not deformed by the pressure.

In order to e.g. increase the area of engagement between the spring and the deformable material, the piston may further comprise a number of flat supporting means positioned between the elastically deformable material and the spring, the supporting means being rotatable along an interface between the spring and the elastically deformable materialr

Preferably, the supporting means are adapted to rotate from a first position to a second position where, in the first position, an outer boundary thereof may be comprised within the first cross-sectional area and where, in the second position, an outer boundary thereof may be comprised within the second cross-sectional area.

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 from a first longitudinal position to a second longimdinal 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. Thus, alternatively to the combinations where the piston adapts to the cross-sectional changes of the chamber, this aspect relates to a chamber having adapting capabilities.

Naturally, 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.

Preferably, 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.

In that manner, 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.

It is clear that depending on from where the combination is seen, 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 function of the combination.

Naturally, 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. In fact, 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 deteraiining 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.

In fact, 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.

If the piston pump is a handpump for tire inflation purposes it can have an integrated connector according to those disclosed in PCT/DK96/00055 (including the US Continuation in Part of 18 April 1997), PCT/DK97/00223 and/or PCT/DK98/00507. The connectors can have an integrated pressure gauge of any type. In a piston pump according to the invention used as e.g. a floor pump or 'carpump' for inflation purposes a pressure gauge arrangement can be integrated in this pump.

Certain piston types as e.g. those of Fig. 4A-F, 7A-E,7J, 12A-C may be combined with any type of chamber.

The combination of certain mechanical pistons as e.g. the one shown in Fig. 3A-C, and and of certain composite pistons as e.g. the one shown in Fig. 6D-F and chambers having a constant circumferical length of the convex type as e.g. the one shown in Fig. 7L may be a good combination.

The combination of composite pistons as e.g. those shown in Fig. 9-12 may be used well with chambers of a convex type, irrespective of a possible change in the circumferical length.

Pistons of the 'embrella type' shown in this application have their open side at the side where the pressure of the medium in the chamber is loading the 'embrella' at the open side. It may also very well possible that the 'embrella' is working upside down.

The inflatable pistons with a skin with a fiber architecture which has been shown have an overpressure in the piston in relation to the pressure in the chamber. It is however also possible to have an equal or lower pressure in the piston than in the chamber - the fibers are than under pressure instead of under tension. The resulting shape may be different than those which are shown in the drawings. In that case, any loading regulating means may have to be tuned differently, and the fibers may have to be supported. The load regulating means showed in e.g. Fig. 9D or 12B may then be constructed so that the movement of the piston of the means gives a suction in the piston, e.g. by an elongation of the piston rod, so that the pistons are now at the other side of the holes in the piston rod. The change in the form of the piston is than different and a collaps may be obtained. This may reduce the life-time. Through these embodiments, reliable and inexpensive pumps optimized for manual operation, e.g. universal bike pumps to be operated by women and teenagers, can be obtained. The shape of the walls of the pressurizing chamber (longitudinal and/or transversal cross-section) and/or piston means of the pumps shown are examples and may be changed depending on the pump design specification. The invention can also be used with all kinds of pumps, e.g. multiple-stage piston pumps as well as with dual-function pumps, piston pumps driven by a motor, pumps where e.g. only the chamber or piston is moving as well as types where both the chamber and the piston are moving simultaneously. Any kind of medium may be pumped in the piston pumps. Those pumps may be used for all kinds of applications, e.g. in pneumatic and/or hydraulic applications. And, the invention is also applicable for pumps which are not manually operated. The reduction of the applied force means a substantial reduction of investments for equipment and a substantial reduction of energy during operation. The chambers may be produced e.g. by injection molding, from taper swaged tubes etc.

In a piston pump a medium is sucked into a chamber which may thereafter be closed by a valve arrangement. The medium is compressed by the movement of the chamber and/or the piston and a valve may release this compressed medium from the chamber. In an actuator a medium may be pressed into a chamber through a valve arrangement and the piston and/or the chamber is moving, initiating the movement of an attached devise. In shock absorbers the chamber may be completely closed, wherein the chamber a compressible medium can be compressed by the movement of the chamber and/or the piston. In the case of a non-compressible medium is inside the chamber, e.g. the piston may be equipped with several small channels which give a dynamic friction, so that the movement is slowed down.

Further, the invention can also be used in propulsion applications where a medium may be used to move a piston and/or a chamber, which can turn around an axis as e.g. in a motor. The above combinations are applicable on all above mentioned applications. Thus, 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. In one situation, the engaging means may have an outer position where the piston is in its first longimdinal 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.

In another situation, 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.

In the situation where the pump is adapted for standing on the floor and the piston/engaging means to compress fluid, such as air, by being forced downwards, the largest force may, ergonomically, be provided at the lowest position of the piston/engaging means/handle. Thus, in the first situation, this means that the highest pressure is provided there. In the second situation, this merely means that the largest area and thereby the largest volume is seen at the lowest position. However, due to the fact that a pressure exceeding that in the e.g. tyre is required in order to open the valve of the tyre, 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 (See Fig. 2B).

Also, 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.

Also, the absorber may comprise a fluid exit connected to the chamber and comprising a valve means. It may be preferred that 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.

Normally, the absorber would comprise means for biasing the piston toward the first longitudinal position.

Finally, the invention also 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.

Also, a fluid exit connected to the chamber and comprising a valve means may be provided. Additionally, the actuator may comprise means for biasing the piston toward the first or second longitudinal position.

207 SPECIFICALLY PREFERRED EMBODIMENTS

According to an embodiment of the invention, there is provided 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 area thereof and, at a second longitudinal position thereof, a second cross-sectional area, the second cross-sectional area being 95% or less of the first cross-sectional area, the change i cross-section 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.

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

Preferably, the second cross-sectional area is approximately 50% of the first cross- sectional area. Preferably the piston comprises: a plurality of at least substantially stiff support members rotatably fastened to a common member, elastically deformable means, supported by the supporting members, for sealing against an inner wall of the chamber the support members being rotatable between 10° and 40° relative to the longitudinal axis.

According to an embodiment of the invention there is also provided a combination where the support members are rotatable so as to be at least approximately parallel to the longitudinal axis. Preferably the common member is attached to a handle for use by an operator, wherein the support members extend, in the chamber, in a direction relatively away from the handle.

Preferably the combination further comprises means for biasing the support embers against an inner wall of the chamber.

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

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

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

Preferably at least part of the deformable material is compressible and wherein the first shape has an area being larger than an area of the second shape.

Preferably the deformable material is at least substantially incompressible.

Preferably the piston comprises a chamber communicating with the deformable container, the chamber having a variable volume.

Preferably the volume may be varied by an operator.

Preferably the chamber comprises a spring-biased piston. Preferably the combination further comprises means for defining the volume of the chamber so that a pressure of fluid in the chamber relates to a pressure of fluid between the piston and the second longitudinal position of the container.

Preferably the defining means are adapted to define the pressure in the chamber at least substantially identical to the pressure between the piston and the second longitudinal position of the container.

Preferably the first cross-sectional shape is 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.

Preferably the first cross-sectional area is at least 5%, preferably at least 10%, such as at least 20%, preferably at least 30%, such as at least 40%, preferably at least 50%, such as at least 60%, preferably at least 70%, such as at least 80%, such as at least 90% larger than the second cross-sectional area.

Preferably 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.

Preferably 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.

Preferably, in the cross-section at the first longitudinal position, a first circumference of the chamber is 80-120%, such as 85-115%, preferably 90-1 10, such as 95-105, preferably 98-102%) of a second circumference of the chamber in the cross-section at the second longitudinal direction.

Preferably the first and second circumferences are at least substantially identical.

Preferably the piston comprises: an elastically deformable material 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, and a coiled flat spring having a central axis at least substantially along the longitudinal axis, the spring being positioned adjacently to the elastically deformable material so as to support the elastically deformable material in the longitudinal direction.

Preferably the piston further comprises a number of flat supporting means positioned between the elastically deformable material and the spring, the supporting means being rotatable along an interface between the spring and the elastically deformable material. Preferably the supporting means are adapted to rotate from a first position to a second position where, in the first position, an outer boundary thereof may be comprised within the first cross-sectional area and where, in the second position, an outer boundary thereof may be comprised within the second cross-sectional area.

According to an embodiment of the invention, there is provided 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 area thereof and, at a second longitudinal position thereof, 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, 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, the piston comprising: a plurality of at least substantially stiff support members rotatably fastened to a common member, elastically deformable means, supported by the supporting members, for sealing against an inner wall of the chamber the support members being rotatable between 10° and 40° relative to the longitudinal axis.

According to an embodiment, there is provided a combination where the support members are rotatable so as to be at least approximately parallel to the longitudinal axis. Preferably the common member is attached to a handle for use by an operator, and wherein the support members extend, in the chamber, in a direction relatively away from the handle.

Preferably, the combination further comprises means for biasing the support members against an inner wall of the chamber 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 area thereof and, at a second longitudinal position thereof, 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, 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 the piston comprising an elastically deformable container comprising a deformable material.

Preferably the deformable material is a fluid or a mixture of fluids, such as water, steam, and/or gas, or a foam. Preferably, in a cross-section through the longitudinal direction, the container has a first shape at the first longitudinal direction and a second shape at the second longitudinal direction, the first shape being different from the second- shape.

Preferably the deformable material is at least substantially incompressible.

Preferably the volume may be varied by an operator.

Preferably the chamber comprises a spring-biased piston.

Preferably, the combination further comprises means for defining the volume of the chamber so that a pressure of fluid in the chamber relates to a pressure of fluid between the piston and the second longitudinal position of the container. Preferably the defining means are adapted to define the pressure in the chamber at least substantially identical to the pressure between the piston and the second longitudinal position of the container.

Preferably the container comprises an elastically deformable material comprising enforcement means.

Preferably the enforcement means comprise fibres. Preferably the foam or fluid is adapted to provide, within the container, a pressure higher than the highest pressure of the surrounding atmosphere during translation of the piston from the first longitudinal position to the second longitudinal position or vice versa. Preferably, 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.

Preferably the first cross-sectional area is at least 5%, preferably at least 10%, such as at least 20%, preferably at least 30%, such as at least 40%, preferably at least 50%, such as at least 60%, preferably at least 70%, such as at least 80, such as at least 90% larger than the second cross-sectional area.

Preferably, in the cross-section at the first longitudinal position, 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.

Preferably the piston comprises: a plurality of at least substantially stiff support members rotatably fastened to a common member, elastically deformable means, supported by the supporting members, for sealing against an inner wall of the chamber.

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

According to another embodiment of the invention, there is provided 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 area thereof and, at a second longitudinal position thereof, 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, the piston comprising: an elastically deformable material 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, and - a coiled flat spring having a central axis at least substantially along the longitudinal axis, the spring being positioned adjacently to the elastically deformable material so as to support the elastically deformable material in the longitudinal direction.

Preferably the piston further comprises a number of flat supporting means positioned between the elastically deformable material and the spring, the supporting means being rotatable along an interface between the spring and the elastically deformable material.

Preferably the supporting means are adapted to rotate from a first position to a second position where, in the first position, an outer boundary thereof may be comprised within the first cross-sectional area and where, in the second position, an outer boundary thereof may be comprised within the second cross-sectional area.

According to an embodiment of the invention there is provided 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 from a first longitudinal position to a second 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.

Preferably the piston is made of an at least substantially incompressible material.

Preferably the piston has, in a cross section along the longitudinal axis, a shape tapering in a direction from to the second longitudinal positions.

Preferably the chamber comprises: 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.

According to an embodiment of the invention, there is provided a pump for pumping a fluid, the pump comprising: a combination according to any of the preceding claims, 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.

Preferably 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.

Preferably the engaging means 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.

According to an embodiment of the invention, there is provided a shock absorber comprising: a combination as described above, 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.

Preferably the shock absorber further comprises a fluid entrance connected to the chamber and comprising a valve means.

Preferably the shock absorber further comprises a fluid exit connected to the chamber and comprising a valve means. Preferably 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.

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

According to an embodiment of the invention there is also provided an actuator comprising: a combination as described above, means for 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.

Preferably the actuator further comprises a fluid entrance connected to the chamber and comprising a valve means. Preferably the actuator further comprises a fluid exit connected to the chamber and comprising a valve means.

Preferably the actuator further comprises means for biasing the piston toward the first or second longitudinal position.

Preferably the introducing means comprise means for introducing pressurised fluid into the chamber. Preferably the introducing means are adapted to introduce a combustible fluid, such as gasoline or diesel, into the chamber, and wherein the actuator further comprises means for combusting the combustible fluid.

Preferably the actuator according further comprises a crank adapted to translate the translation of the piston into a rotation of the crank.

207-1 SPECIFICALLY PREFERRED EMBODIMENTS

According to an embodiment of the invention, there is provided a piston-chamber combination comprising an elongate chamber (70) which is bounded by an inner chamber wall (71,73,75) and comprising a piston means (76,76', 163) in said chamber, the piston means comprising sealing means 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 at the first and second longitudinal positions of said chamber and at least substantially continuously differing cross-sectional areas 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 means being designed to adapt itself and said sealing means to said different cross-sectional areas of said chamber during the relative movements of said piston means from the first longitudinal position through said intermediate longitudinal positions to the second longitudinal position of said chamber, wherein the cross-sections of the different

cross-sectional areas have different cross-sectional shapes, the change in cross-sectional shape of the chamber (162) being continuous between the first and second longitudinal positions of the chamber (162), wherein the piston means (163) is further designed to adapt itself and the sealing means to the different cross-sectional shapes, and wherein a first circumferential length of the cross-sectional shape of the cylinder (162) at the first longitudinal position thereof amounts to 80-120% of a second circumferential length of the cross-sectional shape of the chamber (162) at the second longitudinal position thereof. Preferably is the cross- sectional shape of the chamber (162) at the first longitudinal position thereof is at least substantially circular and wherein the cross-sectional shape of the chamber (162) at the second longitudinal position thereof 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. Preferably is the cross- sectional shape of the chamber (162) at the first longitudinal position thereof is at least substantially circular and wherein the cross-sectional shape of the chamber (162) at the second longitudinal position thereof comprises two or more at least substantially elongate, such as lobe-shaped, parts.

Preferably is a

first circumferential length of the cross-sectional shape of the cylinder (162) at the first longitudinal position thereof amounts to 85-115%, preferably 90-1 10, such as 95-105, preferably 98-102%), of a second circumferential length of the cross-sectional shape of the chamber (162) at the second longitudinal position thereof. Preferably is the first and

second circumferential lengths are at least substantially identical.

Preferably is the

cross-sectional area of said chamber at the second longitudinal position thereof is 95% or less of the cross-sectional area of said chamber (162)at the first longitudinal position thereof. Preferably is the cross- sectional area of said chamber (162) at the second longitudinal

position thereof is between 95% and 15% of the cross-sectional

area of said chamber (162)at the first longitudinal position

thereof.

Preferably is the cross- sectional area of said chamber (162) at the second longitudinal

position thereof is 95-70% of the cross-sectional area of said

chamber (162) at the first longitudinal position thereof.

position thereof is approximately 50% of the cross-sectional

area of said chamber (162) at the first longitudinal position

thereof.

According to an embodiment of the invention there is also provided a pump for pumping a fluid, the pump comprising:

a combination according to any of the preceding claims,

means for engaging the piston means (76, 163) from a

position outside the chamber (162),

a fluid entrance connected to the chamber and comprising a

valve means, and a fluid exit connected to the chamber

(162).

Preferably are the engaging means

have an outer position where the piston means (76, 163) is at

the first longitudinal position of the chamber, and an inner

position where the piston means (76, 163) is at the second

longitudinal position of the chamber ( 162).

Preferably is the engaging means

have an outer position where the piston means (76, 163) is at

the second longitudinal position of the chamber, and an inner position where the piston means is at the first longitudinal

position of the chamber (162).

According to an embodiment of the invention there is also provided a shock absorber comprising:

a combination according to any of claims 1 to 9,

means for engaging the piston means (76, 163) from a

position outside the chamber, wherein the engaging means have

an outer position where the piston means is at the first

longitudinal position of the chamber (162), and an inner

position where the piston means is at the second longitudinal

position.

Preferably a shock absorber which is further comprising

a fluid entrance connected to the chamber (162) and comprising

a valve means.

Preferably a shock absorber which is further

comprising a fluid exit connected to the chamber (162) and

comprising a valve means.

Preferably is

the chamber (162) and the piston means (76, 63) form

an at least substantially sealed cavity comprising a fluid, the

fluid being compressed when the piston means moves from the

first to the second longitudinal positions of the chamber

(162).

Preferably a shock absorber which is

further comprising means for biasing the piston means toward

the first longitudinal position of the chamber.

According to an embodiment of the invention there is also provided

an actuator comprising:

a combination according to any of claims 1 to 9, means for engaging the piston means from a position outside the chamber (162),

means for introducing fluid into the chamber (162) in

order to displace the piston means (76, 163) between the first and the second longitudinal positions of the chamber.

Preferably is an actuator which is further comprising a

fluid entrance connected to the chamber (162) and comprising a valve means.

Preferably is an actuator which is further comprising

a fluid exit connected to the chamber and comprising a valve means. Preferably is an actuator which is further

comprising means for biasing the piston means (76, 163) toward the first or second longitudinal position of the chamber.

Preferably is an actuator which is wherein

the introducing means comprise means for introducing

pressurised fluid into the chamber (162).

Preferably is an actuator which is wherein

the introducing means are adapted to introduce a combustible fluid, such as gasoline or diesel, into the chamber (162), and wherein the actuator further comprises means for combusting the combustible fluid.

Preferably is an actuator which is further

comprising a crank adapted to translate the translation of the piston means into a rotation of the crank. 653 SUMMARY OF THE INVENTION

In the first aspect, 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.

In the present context, the cross-sections are preferably taken perpendicularly to the longitudinal axis (= transversal direction).

Preferably, the second cross-sectional area is 98-5%, such as 95-70% of the first cross- sectional area. In certain situations, the second cross-sectional area is approximately 50% of the first cross-sectional area.

A number of different technologies may be used in order to realise this combination. These technologies are described further in relation to the subsequent aspects of the invention. One such technology is one wherein the piston comprises a container comprising a deformable material.

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

Thus the container may be adjustable to provide sealing to the wall of the chamber having different cross-sectional area's and different circumpherential sizes. This may be achieved by choosing the production size (stress free, undeformed) of the piston approximately equivalent to the circumpherencial length of the smallest cross-sectional area of a cross- section of the chamber, and to expand it when moving to a longitudinal position with a bigger circumpherential length and to contract it when moving in the opposite direction.

And this may be achieved by providing means to keep a certain sealing force from the piston on the wall of the chamber: by keeping the internal pressure of the piston on (a) certain predetennined level(s), which may be kept constant during the stroke. 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. by using a valve for inflation purposes. In the case when spring-force operated devices are being used to obtain the pressure, a valve may not be necessary. When the cross-sectional area of the chamber changes, the volume of the container may change. Thus, in a cross-section through the longitudinal direction of the chamber 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. In one situation, at least part when the deformable material is compressible and the first shape has an area being larger than an area of the second shape. In that situation, the overall volume of the container changes, whereby the fluid should be compressible. Alternatively or optionally, 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.

Also, 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.

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. However, 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. By providing means for defining the volume of the enclosed space communicating with the chamber. In this manner, the pressure of the deformable container may be varied in order to obtain a suitable sealing. For example, 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).

In fact, the use of 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.

It may be possible that the piston does not have or communicate (closed system) or does have or communicate with a valve for inflation. When the piston does not have an inflation valve, 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. When the piston does have an inflation valve 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 independent 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.

When the enclosed space is divided up into a first and second enclosed space, 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. For inflation of the container 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.

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. When 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. The movement of 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. Another solution is that of a comparable solution of the closable bypass of the outlet valve of the chamber - 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.

The above mentioned solutions are applicable too to any pistons comprising a container, incl. those shown in WO 00/65235 and WO 00/70227.

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.

Withstanding the influence of a pressure in the chamber on the piston in order to limit the contact length (longitudinal stretching) may also be done by choosing a suitable reinforcement. 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. When the container has its production size, not only the elastic material of the wall, but also the reinforcement is stress free and undeformed. Expansion of the reinforced wall of the container means that the distance between the crossings (= stitch size) may become larger as the threads expand, while contraction makes the stitch size smaller as the threads contract. 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 j arnming.

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. 1-2 minutes the oven may be opened and the ready produced container wall with the two caps vulcanised in that wall. In order to use 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.

Production of the fiber reinforced wall of the container may be done similar. The reinforced fibers may be produced by e.g. injection moulding, incl. an assembling socket or 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 analogous with the above mentioned ones regarding 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. When inflatable, 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.

Thus, alternatively to the combinations where the piston adapts to the cross-sectional changes of the chamber, this aspect relates to a chamber having adapting capabilities.

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. In that manner, 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.

In yet another aspect, 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 longi dinal 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 mamtaining the preferred smooth variations of the surface in the chamber.

In the present context, the shape of a cross-section is the overall shape thereof - notwimstanding the size thereof. Two circles have the same shape even though one has a diameter different from that of the other.

Preferably, 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. In a preferred embodiment, 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.

Alternatively, 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.

It is clear that depending on from where the combination is seen, 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 functioning 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.

Naturally, 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. In fact, 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.

In fact, 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. The preferred embodiments of the combination of a chamber and a piston have been described as examples to be used in piston pumps. This however should not limit the coverage of this invention to the said application, as it may be mainly the valve arrangement of the chamber besides the fact which item or medium may initiate the movement, which may be decisive for the type of application: pump, actuator, shock absorber or motor. In a piston pump a medium may be sucked 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. In an actuator 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. In shock absorbers the chamber may be completely closed, wherein a compressible medium may be compressed by the movement of the chamber and/or the piston. In the case a non-compressible medium may be positioned inside the chamber, e.g. the piston may be equipped by several small channels which may give a dynamic friction, so that the movement may be slowed down.

Further 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 principles of the invention may also be used in other pneumatic and/or hydraulic applications than the above mentioned piston pumps. Thus, 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.

In one situation, 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.

In the situation where the pump is adapted for standing on the floor and the piston/engaging means to compress fluid, such as air, by being forced downwards, the largest force may, ergonomically, be provided at the lowest position of the piston/engaging means/handle. Thus, in the first situation, this means that the highest pressure is provided there. In the second situation, this merely means that the largest area and thereby the largest volume is seen at the lowest position. However, due to the fact that a pressure exceeding that in the e.g. tyre is required in order to open the valve of the tyre, 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.

As 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. Also, in the case of pumping a liquid when the pressure difference is almost zero, 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. Also the cylinder at the outside may be cylindrical or tapered as well.

Also, 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. Also, the absorber may comprise a fluid exit connected to the chamber and comprising a valve means.

It may be preferred that 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.

Also, 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.

Also, a fluid exit connected to the chamber and comprising a valve means may be provided.

Additionally, 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.

Finally, the invention also relates to a power unit, which preferably may be movable, e.g. by parachute - a M(ovable) P(ower) U(nit). Such a 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. There may be at least one service device present, such as e.g. a pump according to the invention, and/or any other device utilising the excess energy derived from the low working force of a device comprising a combination of a piston and a chamber according to the invention. Due to the very low working force it may be possible to transport a MPU by parachute, as the construction of devices based on the invention may be constructed with lighter weight than those based on the classic piston-cylinder combination. The various embodiments described above are provided by way of illustration only and should not be construed to limit the invention. Those skilled in the art will readily recognize various modifications, changes, and combinations of elements which may be made to the present invention without strictly following the exemplary embodiments and applications illustrated and described herein, and without departing from the true spirit and scope of the present invention.

653 SPECIFICALLY PREFERRED EMBODIEMENTS

According to an embodiment of the invention, there is provided 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 wall at least between a first longitudinal position and a second longitudinal position of the chamber, said chamber having cross- sections of different cross-sectional areas and different circumferential lengths at the first and second longitudinal positions, and at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longitudinal position, said piston comprising a container which is elastically deformable thereby providing for different cross-sectional areas and circumferential lengths of the piston adapting the same to said different cross-sectional areas and different circumferential lengths of the chamber during the relative movements of the piston between the first and second longitudinal positions through said intermediate longitudinal positions of the chamber, wherein: the piston is produced to have a production-size of the container in the stress-free and undeformed state thereof in which the circumferential length of the piston is approximately equivalent to the circumferential length of said chamber (162,186,231) at said second longitudinal position, the container being expandable from its production size in a direction transversally with respect to the longitudinal direction of the chamber thereby providing for an expansion of the piston from the production size thereof during the relative movements of the piston from said second longitudinal position to said first longitudinal position.

Preferably is the container inflatable and said container being elastically deformable and being inflatable to provide for different cross-sectional areas and circumferential lengths of the piston.

Preferably is the cross-sectional area of said chamber at the second longitudinal position thereof between 98 % and 5 % of the cross-sectional area of said chamber at the first longitudinal position thereof. Preferably is the cross-sectional area of said chamber at the second longitudinal position thereof 95 - 15 % of the cross-sectional area of said chamber at the first longitudinal position thereof.

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

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

Preferably is the deformable material comprising spring-force operated devices, such as springs. Preferably has in a cross-section through the longitudinal direction, the container, when being positioned at the first longitudinal position of the chamber, a first shape which is different from a second shape of the container when being positioned at the second longitudinal position of said chamber. Preferably is at least part of the deformable material compressible and wherein the first shape has an area being larger than an area of the second shape.

Preferably is the deformable material is at least substantially incompressible. Preferably is the container inflatable, to a certain pre-determined pressure value. Preferably is the pressure remaining constant during the stroke. Preferably is the piston comprising an enclosed space communicating with the deformable container, the enclosed space having a variable volume.

Preferably is the volume of the enclosed space adjustable.

Preferably is the first enclosed space comprising a spring-biased pressure tuning piston.

Preferably further comprising means for defining the volume of the first enclosed space so that the pressure of fluid in the first enclosed space relates to the pressure in the second enclosed space.

Preferably the defining means are adapted to define the pressure in the first enclosed space during the stroke.

Preferably are the defining means adapted to define the pressure in the first enclosed space at least substantially constant during the stroke.

Preferably is the spring-biased pressure tuning piston a check valve through which fluid of an external pressure source can flow into the first enclosed space. Preferably can the fluid from an external pressure source enter the second enclosed space through an inflation valve, preferably a valve with a core pin biased by a spring, such as a Schrader valve from an external pressure source.

Preferably is the piston communicating with at least one valve.

Preferably is the piston comprising a pressure source.

Preferably is the valve an inflation valve, preferably a valve with a core pin biased by a spring, such as a Schrader valve. Preferably is the valve a check valve.

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

Preferably is the outlet valve an inflation valve, preferably a valve with a core pin biased by a spring, such as a Schrader valve, said core pin is moving towards the chamber when closing the valve. Preferably is the core pin of the valve connected to an actuator which opens or close the valve.

Preferably is the actuator a valve actuator for operating with valves having a spring-force operated valve core pin, comprising a housing to be connected to a pressure medium source, within the housing a coupling section for receiving the valve to be actuated, a cylinder surrounded by a cylinder wall of a predetermined cylinder wall diameter and having a first cylinder end and a second cylinder end which is farther away from the coupling section than the first cylinder end, a piston which is movably located in the cylinder and fixedly coupled to an activating pin for engaging with the spring-force operated valve core pin of the valve received in the coupling section, and a conducting channel, for conducting pressure media from the cylinder to the coupling section when the piston is moved into a first piston position in which the piston is at a first predetermined distance from the first cylinder end, the conduction of the pressure media between the cylinder and the coupling section being inhibited when the piston is moved into a second piston position in which the piston is at a second predermined distance from the first cylinder end which second distance being larger than said first distance, wherein the conducting channel is arranged in the cylinder wall and opens into the cylinder at a cylinder wall portion having the predetermined cylinder wall diameter, and the piston comprises a piston ring with a sealing edge which sealingly fits with said cylinder wall portion thereby inhibiting the conduction of the pressure medium into the channel in the second position of the piston and opening the channel in the first position of the piston. Preferably is the actuator is a valve actuator for operating with valves having a spring-force operated valve core pin, comprising a housing to be connected to a pressure medium source, within the housing a coupling section for receiving the valve to be actuated, a cylinder circumferentially surrounded by a cylinder wall of a predetermined cylinder wall diameter and having a first cylinder end and a second cylinder end which is farther away from the coupling section than said first cylinder end and is connected to the housing for receiving pressure medium from said pressure source, a piston which is movably located in the cylinder and fixedly coupled to an activating pin for engaging with the spring-force operated valve core pin of the valve received in the coupling section, and a conducting channel between said second cylinder end and said coupling section for conducting pressure medium from said second cylinder end to the coupling section when the piston is moved into a first piston position in which the piston is at a first predetermined distance from said first cylinder end, said conduction of pressure medium between said second cylinder end and the coupling section being inhibited when the piston is moved into a second piston position in which the piston is at a second predermined distance from said first cylinder end which second distance being larger than said first distance, the conducting channel is arranged in said cylinder wall and has a channel portion which opens into the cylinder at a cylinder wall portion having said predetermined cylinder wall diameter, and the piston comprises a piston ring with a sealing edge which sealingly fits with said cylinder wall portion, said sealing edge of the piston ring being located between said channel portion and said second cylinder end in said second piston position, thereby inhibiting said conduction of the pressure medium from said second cylinder end into the channel in said second piston position, and being located between said channel portion and said first cylinder end in said first piston position, thereby opening the channel to said second cylinder end in said first piston position.

Preferably is the activator an actuator valve for a container type piston pressure management system that selectively feeds pressurized air to the interior of a container type piston, said valve comprising, a valve body with a cylindrical central passage opening both to said pressurized fluid and to the interior of said container type piston, a spring loaded check valve tightly received in said central passage that blocks said central passage when closed and allows flow of fluid through when opened, a spring loaded piston slidably received within said passage above said check valve that slides from an off-position toward said check valve to an on-position when said pressurized fluid is supplied and off again when said pressurized fluid is removed, said piston engaging the surface of said central passage with sufficient clearance to allow unrestricted sliding, but not closely enough to prevent the leakage of pressurized fluid between said piston and central passage surface, a stem carried by said piston and engageable with said check valve to open it and allow the passage of pressurized fluid to said check valve and to said container type piston interior as said piston moves to the on-position, a stationary plug in said central passage between said check valve and piston through which said stem extends that is normally axially spaced from said piston but abuts said piston in its on-position, said plug having a vent path running from atmosphere into the space between said plug and piston at a vent point radially near said stem so that pressurized fluid leaking past said piston as it moves will not compress between said plug and piston to retard its motion, and, a circular compression seal surrounding said vent point that is compressed between said piston and plug when they are abutted so that pressurized air leaking past said piston can not vent to atmosphere when said check valve is open.

Preferably is the activator an actuator valve for a container type piston pressure management system that selectively feeds pressurized fluid to the interior of said container type piston, said valve comprising, a valve body with a cylindrical central passage opening both to said pressurized fluid and to the interior of said container type piston, a spring loaded check valve tightly received in said central passage that blocks said central passage when closed and allows flow of fluid through when opened, a spring loaded piston slidably received within said passage above said check valve that slides from an off-position toward said check valve to an on-position when said pressurized fluid is supplied and off again when said pressurized fluid is removed, said piston engaging the surface of said central passage with sufficient clearance to allow unrestricted sliding, but not closely enough to prevent the leakage of pressurized fluid between said piston and central passage surface, a stem carried by said piston and engageable with said check valve to open it and allow the passage of pressurized fluid to said check valve and to said container type piston interior as said piston moves to the on-position, an outer annular disk and an inner annular disk abutted in said central passage to form a plug between said check valve and piston through which said stem extends, said piston being normally axially spaced from said outer disk but abutted therewith in its on-position, said outer disk having a series of holes radially close to said stem opening to a series of notches in said inner disk to create a vent path running from the atmosphere into the space between said plug and piston so that pressurized fluid leaking past said piston as it moves will not compress between said plug and piston to retard its motion, and, a circular compression seal surrounding said holes that is compressed between said piston and plug when they are abutted so that pressurized fluid leaking past said piston cannot vent to the atmosphere when said check valve is open. Preferably is an activating pin for connecting to inflation valves, comprising a housing to be connected to a pressure source, within the housing a connection hole having a central axis and an inner diameter approximately corresponding to the outer diameter of the inflation valve to which the activating pin is to be connected, and a cylinder and means for conducting liquid media between the cylinder and the pressure source, and where the activating pin is arranged to engage a central spring- force operated core pin of the inflation valve, is arranged to be situated within the housing in continuation of the coupling hole coaxially with the central axis thereof, and comprises a piston part with a piston, which piston is to be positioned in the cylinder movable between a first piston position and a second piston position, the activating pin comprising a channel, said piston part comprises a first end and a second end, wherein the piston is located at said first end and said channel has an opening at said first end, a valve part being movable in the channel, derivable by difference in forces acting on surfaces of the valve part, between a first valve position and a second valve position, wherein said first valve position leaves said opening open, and said second valve position closes said opening, and the top of the piston part forming a valve seat for a seal face of the valve the valve means.

Preferably is the valve actuator an activating pin for connecting to inflation valves, comprising a housing, within the housing a coupling hole for coupling with an inflation valve, the coupling hole having a central axis and an outer opening, positioning means for positioning the inflation valve when coupled in the coupling hole, and an activating pin, which is arranged coaxially with the coupling hole, for depressing a central spring-force operated core pin of the inflation valve, a cylinder having a cylinder wall provided with a pressure port which is connected to a pressure source, wherein the activating pin is shiftable between a proximal pin position and a distal pin position relative to the positioning means so as to depress the core pin of the inflation valve in its distal pin position and disengage the core pin of the inflation valve in its proximal pin position when the inflation valve is positioned by the positioning means, the activating pin is coupled with a piston and the piston is slidingly arranged in the cylinder and is movable between a proximal piston position, which corresponds to the proximal pin position, and a distal piston position, which corresponds to the distal pin position, the piston is disposed in the cylinder between the pressure port and the coupling hole and is drivable from its proximal piston position to its distal piston position by the pressure supplied into the cylinder from the pressure source, and - that flow regulating means are provided for selectively interrupting or freeing a flow path between the pressure source and the coupling hole depending on the piston positions and are adapted such that the flow path is interrupted in the proximal piston position and the flow path is freed in the distal piston position at least when the inflation valve is positioned by the positiomng means .

Preferably is the piston comprising means to obtain a pre-determined pressure level. Preferably is the valve a release valve.

Preferably is a spring-force operated cap which closes the channel above the valve actuator when the pressure comes above a certain pre-determined pressure value. Preferably is a channel be opened or closed, the channel connects the chamber and the space between the valve actuator and the core pin, a piston is movable between an opening position and a closing position of said channel, and the movement of the piston is controlled by an actuator which is steered as a result of a measurement of the pressure in the piston. Preferably is a channel be opened or closed, which connects the chamber and the space between the valve actuator and the core pin.

Preferably is a piston movable between an opening position and a closing position of said channel.

Preferably is the piston operated by a operator controlled pedal, which is turning around an axle from a inactive position to an activated position and vice versa.

Preferably is the piston controlled by an actuator which is steered as a result of a measurement of the pressure in the piston.

Preferably is the combination further comprising means for defining the volume of the enclosed space so that the pressure of fluid in the enclosed space relates to the pressure acting on the piston during the stroke.

Preferably is the foam or fluid adapted to provide, within the container, a pressure higher than the highest pressure of the surrounding atmosphere during translation of the piston from the second longitudinal position of the chamber to the first longitudinal position thereof or vice versa. Preferably is the combination comprising a pressure source.

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

Preferably is the pressure source communicating with the container by an outlet valve and an inlet valve.

Preferably is the outlet valve an inflation valve, preferably a valve with a core pin biased by a spring, such as a Schrader valve, said core pin is moving towards the pressure source when closing the valve. Preferably is the inlet valve an inflation valve, preferably a valve with a core pin biased by a spring, such as a Schrader valve, said core pin is moving towards the container when closing the valve.

Preferably is a channel be opened or closed, which connects the chamber and the space between the valve actuator and the core pin.

Preferably is a channel be opened or closed, which connects the chamber and the space between the valve actuator and the core pin. Preferably is a piston movable between an opening position and a closing position of said channel.

Preferably is a channel be opened or closed, the channel connects via the space the chamber and the space between the valve actuator and the core pin, a piston is movable between an opening position and a closing position of said channel, and the movement of the piston is controlled by an actuator which is steered as a result of the measurement of the pressure level in the piston and that of the pressure source.

Preferably is a channel be opened or closed, the channel connects via the space the chamber and the space between the valve actuator and the core pin, a piston is movable between an opening position and a closing position of said channel, and the movement of the piston is controlled by an actuator which is steered as a result of the measurement of the pressure level of the pressure in the and that of the pressure source.

Preferably is the wall of the container comprising an elastically deformable material comprising reinforcement means.

Preferably have the reinforcement windings a braid angle which is different from 54°44'. Preferably is the reinforcement means comprising a textile reinforcement, which enable expansion of the container when moving to a first longitudinal position, and enable contraction when moving to a second longitudinal position.

Preferably is the piston produced by a production system with multiple vulcanisation caves.

Preferably is the reinforcement means comprising fibres, which enable expansion of the container when moving to bigger a first longitudinal position, and enable contraction when moving to a second longitudinal position.

Preferably is the piston produced by a production system with multiple vulcanisation caves and where the fibers are being mounted in the caves of the caps by rotation of the fibers and the cabs at different speeds, while the fibers are being pushed onto the inside of the caps.

Preferably are the fibers arranged as to the Trellis Effect.

Preferably is the reinforcement means comprising a flexible material positioned in the container, comprising a plurality of at least substantially elastic support members rotatably fastened to a common member, the common members connected to the skin of the container.

Preferably are said members and/or the common member inflatable.

Preferably is the pressure on the wall of the container build up by spring-force operated devices.

Preferably is the piston comprising a reinforcement which is positioned outside the container. Preferably is the container moving in a cylinder around a tapered wall. Preferably is the chamber convex and the operating force tangents a set maximum force during the stroke.

According to an embodiment of the invention, there is also provided a combination according to any of the preceeding statements or a combination of a piston comprising a container which has a wall which is bendable, or a combination of a piston comprising a container 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, wherein: the cross-sections of the different cross-sectional areas have different cross-sectional shapes, the change in cross-sectional shape of the chamber being at least substantially continuous between the first and second longitudinal positions of the chamber, wherein the piston is further designed to adapt itself and the sealing means to the different cross-sectional shapes.

Preferably is the cross-sectional shape of the chamber at the first longitudinal position thereof at least substantially circular and wherein the cross-sectional shape of the chamber at the second longitudinal position thereof 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.

Preferably is the cross-sectional shape of the chamber at the first longitudinal position thereof at least substantially circular and wherein the cross-sectional shape of the chamber at the second longitudinal position thereof comprises two or more at least substantially elongate, such as lobe-shaped, parts.

Preferably is a first circumferential length of the cross-sectional shape of the cylinder at the first longitudinal position thereof amounting to 80-120%, such as 85-115%, preferably 90-110, such as 95-105, preferably 98-102%, of a second circumferential length of the cross-sectional shape of the chamber at the second longitudinal position thereof.

Preferably are the first and second circumferential lengths at least substantially identical. According to an embodiment of the invention, there is also provided a piston-chamber combination comprising an elongate chamber bounded by an inner chamber wall and comprising a piston in the chamber to be sealingly movable in the chamber, the piston being movable in the chamber at least from a second second longitudinal position thereof to a first longitudinal position thereof, the chamber comprising an elastically deformable inner wall along at least part of the length of the chamber wall between the first and second longitudinal positions, the chamber having, at the first longitudinal position thereof when the piston is positioned at that position, a first cross-sectional- area, which is larger than a second cross-sectional area at the second longitudinal position of the chamber when the piston is positioned at that position, the change in cross-sections 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 the piston including an elastically expandable container having changeable geometrical shapes which adapt to each other during the piston stroke thereby enabling a continuous sealing, and the piston having its production size when positioned at the second longitudinal position of the chamber.

Preferably is the piston made of an at least substantially incompressible material.

Preferably has the piston, in a cross section along the longitudinal axis, a shape tapering in a direction from the first longitudinal position of the chamber to the second longitudinal position thereof.

Preferably is the angle between the wall and the central axis of the cylinder at least smaller than the angle between the wall of the taper of the piston and the central axis of the chamber. Preferably is the chamber comprising 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.

Preferably is the space defined by the outer structure and the inner wall inflatable. Preferably is the piston comprises an elastically deformable container comprising a deformable material and designed according to statements 7 to 17.

According to an embodiment of the invention, there is provided a pump for pumping a fluid, the pump comprising a combination according to any of the earlier mentioned statements, 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.

Preferably have the engaging means an outer position where the piston is at the first longitudinal position of the chamber, and an inner position where the piston is at the second longitudinal position of the chamber.

Preferably have the engaging means an outer position where the piston is at the second longitudinal position of the chamber, and an inner position where the piston is at the first longitudinal position of the chamber.

According to an embodiment of the invention, there is provided a shock absorber comprising: a combination according to any of the preceeding statements 1-80, means for engaging the piston from a position outside the chamber, wherein the engaging means have an outer position where the piston is at the first longitudinal position of the chamber, and an inner position where the piston is at the second longitudinal position.

Preferably is the shock absorber comprising a fluid entrance connected to the chamber and comprising a valve means.

Preferably is the shock absorber further comprising a fluid exit connected to the chamber and comprising a valve means. Preferably form the chamber and the piston 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 of the chamber. Preferably a shock absorber further comprising means for biasing the piston toward the first longitudinal position of the chamber.

According to an embodiment of the invention, there is provided an actuator comprising: a combination according to any of preceding the statements 1-80, 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 of the chamber.

Preferably an actuator further comprising a fluid entrance connected to the chamber and comprising a valve means.

Preferably an actuator further comprising a fluid exit connected to the chamber and comprising a valve means.

Preferably an actuator further comprising means for biasing the piston toward the first or second longitudinal position of the chamber.

Preferably the introducing means comprise means for introducing pressurised fluid into the chamber.

Preferably are the introducing means adapted to introduce a combustible fluid, such as gasoline or diesel, into the chamber, and wherein the actuator further comprises means for combusting the combustible fluid.

Preferably are the introducing means adapted to introduce an expandable fluid to the chamber, and wherein the actuator further comprises means for expand the expandable fluid. Preferably is the actuator further comprising a crank adapted to translate the translation of the piston into a rotation of the crank. Preferably a motor wherein comprising a combination according to any of the foregoing statements.

Preferably a power unit comprising a combination according to any of the foregoing statements, a power source, and a power device. Preferably is the power unit movable.

653-2 SPECIFICALLY PREFERRED EMBODIMENTS

According to an embodiment of the invention, there is provided 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 wall at least between a first longitudinal position and a second longitudinal position of the chamber, said chamber having cross-sections of different cross- sectional areas and different circumferential lengths at the first and second longitudinal positions, and at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longitudinal position, said piston comprising a container which is elastically deformable thereby providing for different cross-sectional areas and circumferential lengths of the piston adapting the same to said different cross-sectional areas and different circumferential lengths of the chamber during the relative movements of the piston between the first and second longitudinal positions through said intermediate longitudinal positions of the chamber, said container is inflatable and being elastically deformable to provide for different cross-sectional areas and circumferential lengths, wherein said piston is communicating with a- pressure source.

Preferably takes the communication place through an enclosed space, the enclosed space having a variable volume.

Preferably takes the communication place through a valve.

Preferably is the pressure source communicating with the container by an outlet valve and an inlet valve. Preferably is the outlet valve an inflation valve preferably a valve with a core pin biased by a spring, such as a Schrader valve, said core pin is moving towards the pressure source when closing the valve.

Preferably is the inlet valve an inflation valve preferably a valve with a core pin biased by a spring, such as a Schrader valve, said core pin is moving towards the container when closing the valve.

According to an embodiment of the invention there is also provided a valve actuator for operating with valves having a spring-force operated valve core pin, comprising a housing to be connected to a pressure medium source, within the housing a coupling section for receiving the valve to be actuated, a cylinder surrounded by a cylinder wall of a predetermined cylinder wall diameter and having a first cylinder end and a second cylinder end which is farther away from the coupling section than the first cylinder end, a piston which is movably located in the cylinder and fixedly coupled to an activating pin for engaging with the spring-force operated valve core pin of the valve received in the coupling section, and a conducting channel, for conducting pressure media from the cylinder to the coupling section when the piston is moved into a first piston position in which the piston is at a first predetermined distance from the first cylinder end, the conduction of the pressure media between the cylinder and the coupling section being inhibited when the piston is moved into a second piston position in which the piston is at a second predermined distance from the first cylinder end which second distance being larger than said first distance, wherein the conducting channel is arranged in the cylinder wall and opens into the cylinder at a cylinder wall portion having the predetermined cylinder wall diameter, and the piston comprises a piston ring with a sealing edge which sealingly fits with said cylinder wall portion thereby inhibiting the conduction of the pressure medium into the channel in the second position of the piston and opening the channel in the first position of the piston.

Preferably can a channel be opened or closed, which connects the chamber and the space between the valve actuator and the core pin.

Preferably can a channel be opened or closed, the channel connects via the space the chamber and the space between the valve actuator and the core pin, a piston is movable between an opening position and a closing position of said channel, and the movement of the piston is controlled by an actuator which is steered as a result of the measurement of the pressure level in the piston and that of the pressure source.

Preferably can a channel be opened or closed, the channel connects via the space the chamber and the space between the valve actuator and the core pin, a piston is movable between an opening position and a closing position of said channel, and the movement of the piston is controlled by an actuator which is steered as a result of the measurement of the pressure level of the pressure in the piston and that of the pressure source.

Preferably is said enclosed space comprising a first enclosed space. Preferably is said enclosed space comprising a second enclosed space. Preferably comprises the first enclosed space comprises a spring-biased pressure tuning piston. According to an embodiment of the invention there is also provided means for defining the volume of the first enclosed space, so that the pressure of fluid in the first enclosed space relates to the pressure in the second enclosed space.

Preferably is the spring-biased pressure tuning piston a check valve through which fluid of an external pressure source can flow into the first enclosed space.

Preferably enters the fluid from an external pressure source the second enclosed space through an inflation valve, preferably a valve with a core pin biased by a spring, such as a Schrader valve.

Preferably is the piston produced to have a production-size of the container in the stress-free and undeformed state thereof in which the circumferential length of the piston is approximately equivalent to the circumferential length of said chamber at said second longitudinal position, the container being expandable from its production size in a direction transversally with respect to the longitudinal direction of the chamber thereby providing for an expansion of the piston from the production size thereof during the relative movements of the piston from said second longitudinal position to said first longitudinal position,

Preferably is the cross-sectional area of said chamber at the second longitudinal position thereof between 98 % and 5 % of the cross-sectional area of said chamber at the first longitudinal position thereof.

Preferably is a combination wherein the cross-sectional area of said chamber at the second longitudinal position thereof 95 - 15 % of the cross-sectional area of said chamber at the first longitudinal position thereof. Preferably is the cross-sectional area of said chamber at the second longitudinal position thereof approximately 50% of the cross-sectional area of said chamber at the first longitudinal position thereof.

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

Preferably contains the container a deformable material.

Preferably is deformable material a fluid or a mixture of fluids, such as water, steam and/or gas, or a foam. 507 SUMMARY OF THE INVENTION

The valve actuator of the present invention and embodiments thereof are subjects of claims 1 and 2 to 17, respectively. A valve connector and a pressure vessel or hand pump, comprising a valve actuator of the present invention are subjects of claims 18 and 19, respectively. Claim 20 is directed to the use of the valve actuator in a stationary construction.

The present invention provides a valve actuator which comprises an inexpensive combination of a cylinder, within in which -the piston driving the activating pin moves, and an activating pin, having a simple construction. This combination can be used in stationary constructions, such as chemical plants, where the activating pin engages the spring-force operated core pin of a valve (e.g. a release valve), as well as in valve connectors (e.g. for inflating vehicle tires). The disadvantage of conventional valve connectors have been overcome by the valve actuator of the present invention. This valve actuator features a piston having a piston ring fitting into the cylinder, where the piston, in its first position, is at a first predetermined distance from the first end of the cylinder. In the piston's second position, it is at a second predetermined distance from the first end of the cylinder, wherein the second predetermined distance is larger than the first predetermined distance. The cylinder wall comprises a conducting channel for allowing conduction of gaseous and/or liquid media between the cylinder and the coupling section when the piston is in the first position, whereas conduction of gaseous and/or liquid media between the cylinder and the coupling section is inhibited by the piston when the piston is in the second position.

One embodiment of the valve actuator of the present invention according to claim 6 features a conducting channel from the pressure source to the valve to be actuated that comprises an enlargement of the cylinder diameter which is arranged around the piston of the activating pin in the bottom of the cylinder, when the piston is in the first position, enabling the medium from the pressure source to flow to the opened spring-force operated valve core pin, e.g. from a Schrader valve. The enlargement of the cylinder's diameter may be uniform, or the cylinder wall may contain one or several sections near the bottom of the cylinder where the distance between the center line of the cylinder and the cylinder wall increases so that gaseous and/or liquid media can freely flow around the edge of the piston ring when the piston is in the first position. A variant of this embodiment has a valve actuator arrangement of which its cylinder has the enlargement of the diameter twice. The distance between the enlargements can be the same as the distance between the sealing levels of the sealing means. When three valves of different sizes can be coupled the valve actuator may comprise a cylinder with three enlargements. It is however also possible to connect valves of different sizes to a valve actuator having a single arrangement for the enlargement of the diameter of the cylinder. Now therefore the number of enlargements can be different from the number of different valve sizes of valves which can be coupled.

Another embodiment of the present invention according to claim 10 features a conducting channel through a part of the body of the valve actuator. The channel forms a passage for gaseous and/or liquid media between the cylinder and the part of the valve actuator which is coupled to the valve. The orifice of the channel opening in the cylinder is located such that, when the piston is in the first position, pressurized gaseous and/or liquid media flowing from the pressure source to the cylinder may flow further through the channel to the valve to be actuated. When the piston is in the second position, it blocks the cylinder so that the flow of pressurized gaseous and or liquid media into the channel is not possible.

Instead of air, (mixtures of) gases and/or liquids of any kind can activate the activation pin and can flow around the piston of the valve actuator when the piston is in its first position. The invention can be used in all types of valve connectors to which a valve with a spring-force operated core pin (e.g. a Schrader valve) can be coupled irrespective of the method of coupling or the number of coupling holes in the connector. Furthermore the valve actuator can be coupled to for example a foot pump, car pump, or compressor. The valve actuator can also be integrated in any pressure source (e.g. a handpump or a pressure vessel) irrespective of the availability of a securing means in the valve connector. It is also possible for the invention to be used in permanent constructions where the activating pin of the actuator engages the core pin of a permanently mounted valve.

507 SPECIFICALLY PREFERRED EMBODIMENTS

According to an embodiment of the invention, there is provided a valve actuator for operating with valves having a spring-force operated valve core pin, comprising - a housing to be connected to a pressure medium source, within the housing a coupling section for receiving the valve to be actuated, a cylinder surrounded by a cylinder wall of a predetermined cylinder wall diameter and having a first cylinder end and a second cylinder end which is farther away from the coupling section than the first cylinder end, a piston which is movably located in the cylinder and fixedly coupled to an activating pin for engaging with the spring-force operated valve core pin of the valve received in the coupling section, and a conducting channel for conducting pressure media from the cylinder to the coupling section when the piston is moved into a first piston position in which the piston is at a first predetermined distance from the first cylinder end, the conduction of the pressure media between the cylinder and the coupling section being inhibited when the piston is moved into a second piston position in which the piston is at a second predermined distance from the first cylinder end which second distance being larger than said first distance, wherein: the ^" conducting channel is arranged in the cylinder wall and opens into the cylinder at a cylinder wall portion having the predetermined cylinder wall diameter, and the piston comprises a piston ring with a sealing edge which sealingly fits with said cylinder wall portion thereby inhibiting the conduction of the pressure medium into the channel in the second position of the piston and opening the channel in the first position of the piston.

Preferably is said first predetermined distance greater than zero.

Preferably is said first predetermined distance approximately zero. Preferably it is comprising a stopper to limit the movement of the piston in the first piston position.

Preferably it is comprising a tapered portion at the first end of the cylinder and a conical portion of the piston to coincide with said tapered portion when the piston is in the first piston position. Preferably is the conducting channel formed by an enlargement of the cylinder wall diameter which is arranged to be radially around the piston when being in its first piston position so that the pressure medium can freely flow around the edge of the piston ring when the piston is in its first piston position. Preferably is the enlargement of the cylinder diameter formed at one or several sections of the circumference of the cylinder wall.

Preferably is the wall of the enlargement comprising a cylindrical enlargement wall portion and an inclined enlargement wall portion forming an angle with the cylinder axis which is larger than 0° and smaller than 20°, wherein the inclined enlargement wall portion is situated between the cylindrical enlargement wall portion and the cylinder wall portion having the predeteirnined cylinder wall diameter.

Preferably is a channel portion of the conducting channel between the cylindrical enlargement wall portion and the coupling section designed as a tapered channel portion shaped as a groove or is designed as a hole (107) which is parallel to the center axis of the cylinder.

Preferably is the coupling section connected by the conducting channel to an orifice in the cylinder wall portion , said orifice being situated at a distance from the first cylinder end so that the orifice is situated between the piston and the second end of the cylinder when the piston is in the first piston position.

Preferably is the piston further movable within the cylinder to a third position and a fourth position, corresponding to a third predetermined distance and a fourth predetermined distance from the first end of the cylinder, respectively, where said third predetermined distance is larger than said second predetermined distance and said fourth predetermined distance is larger than said third predetermined distance; and - the cylinder comprises a second channel for allowing the conduction of gaseous and/or liquid media between the cylinder and the coupling section when the piston is in said third position and inhibiting the conduction of gaseous and/or liquid media between the cylinder and the coupling section when the piston is in said fourth position. Preferably is the embodiment comprising within the coupling section sealing means for sealing the valve actuator onto valves of different types and/or sizes, and the sealing means comprise a first annular sealing portion and a second annular portion situated coaxially with the centre axis of the coupling section and being displaced in the direction of the centre axis of the coupling section , said first annular portion is closer to the opening of the coupling section than said second annular portion and the diameter of said first annular portion is larger than the diameter of said second annular portion

Preferably is the embodiment comprising within the coupling section a securing thread for securing the valve actuator onto the inflation valve.

Preferably is said securing thread a temporary securing thread .

Preferably is the cylinder wall formed as a cylinder sleeve, fastened and sealed in the housing and formed with said inclined enlargement wall portion , the cylinder sleeve having distant from the first cylinder end a wall portion an angle so that the piston ring is not sealing there.

Preferably is said cylinder sleeve fastened and sealed by a snap-lock in the wall of the housing .

Preferably is the embodiment provided within the coupling section a sealing means for sealing the valve actuator onto a valve with a spring-force operated valve core pin.

According to an embodiment of the invention there is also provided a valve connector, coupled to a handpump, a foot pump, a car pump, a pressure vessel or a compressor, for inflating vehicle tires, comprising a valve actuator of any of claims 1 to 16.

According to an embodiment of the invention there is also provided a pressure vessel or a hand pump for inflating a vehicle tire, wherein: an integrated valve actuator. According to an embodiment of the invention there is also provided a valve actuator in a stationary construction, such as a chemical plant.

19597 SUMMARY OF THE INVENTION

In the first aspect, the invention relates to a combination of a piston and a chamber, 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 wall at least between a first longitudinal position and a second longitudinal position of the chamber, said combination engaging a rigid surface, enabling said movement, where said combination is movable relatively to said surface.

Force providers for enabling the relative movement of the parts of the combination may move themselves, and the path of the last mentioned movement does not at any time comply exactly with the path of the relative movement of the piston rod, the piston and the chamber. Thus the system of the force provider and the combination may provide a flexibility somewhere in the system in order to avoid damage. When the force provider may engaging the combination with changing forces, and which may also keeping the non-moving part of the combination towards a rigid surface, in order to enable said relative movement, there may be conflicting demands towards the combination, if said rigid surface also has the function of providing reaction forces for the combination. The last mentioned may happen when a pump is engaged by a human body, while the pump is being held down to the rigid surface e.g. a floor, by a foot of said user. Specifically when a standing person is using a floor pump for pumping a tire, and specifically if the floor is not in level. The combination ought therefore be movable in relation to the rigid surface, in order to follow the path of the force provider.

In a second aspect is the problem of non-compliance specifically important when a chamber is used with having cross-sections of different cross-sectional areas at the first and second longitudinal positions, and at least substantially continuously different cross- sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional at said first longitudinal position - this is also valid in the case where the cross-sectional area's at the first and second longitudinal position having a different size, but an equal circumferential size.

In an optmized embodiment for obtaining the highest level of reduction of energy, the chamber of e.g. a floor pump for tyre inflation has a smallest possible cross-sectional area at its bottom and a biggest at its top. Thus at the smallest cross-sectional area is the biggest force moment engaging the transition from the chamber to the basis of the pump. The combination should therefore be movable in relation to the rigid surface, in order to follow the path of the force provider. In a third aspect the combination comprises a basis for engaging the combination to a rigid surface, enabling the relative movement of the piston and the chamber, the combination is rigidly fastened to a basis, said basis is movable relatively to said rigid surface.

The basis may have three engaging surfaces on the rigid surface, ensuring a stable positioning of the combination, even the rigid surface would not be flat. The combination may then turn around any line between two of the three engaging surfaces. This however is a poor solution, as the path of a human force provider normally is a 3 -dimensional path. And compensation for a positioning of the combination when said surface is not in level, cannot be obtained by this solution. And, in the case of floor pumps for tyre inflation is normally the foot of a user pressing the basis of the pump towards the rigid surface, which might prohibite said movement(s).

In a fourth aspect the combination comprises a basis for engaging the combination to a rigid surface, enabling the relative movement of the piston and the chamber, the combination is flexibly fastened e.g. by means of an elastically deformable bushing, to said basis.

This solution, combined with a basis with three engaging surfaces, is an optimized solution which complies to all demands: the path of the combination may be any path which is used by the force provider (e.g. user), while the basis is standing on the surface, held down e.g. by the foot of teh user. Not only can a rigid surface, not in level, be compensated, so that the combination, but not the basis, still is beying perpendicular water , the user of the floor pump is able to initiate any path during the stroke. After use may the combination automatically coming back to it rest position, namely perpendicular the rigid surface.

Alternative technical solutions for said bushing are of course possible, e.g. a ball joint at the end of the cylinder, holding within a ball barring of the basis - the ball may be combined with a spring, which limits the deflection of the combination, and returns a deflection to default after use. This solution (not shown) may be more expensive than the bushing. This is also valid for piston-chamber combinations with differing cross-sectional areas and equal of differing cicumferentiual sizes.

The guiding means may be comprising a washer with a small hole with an appropriate fitting with the piston rod, while this washer may be movable within a bigger hole within the cap: the piston rod may mainly translate in a transversal direction of the combination. The washer may come back to its default position by means of a sprong-force e.g. an O- ring between the hole in the cab, and the outside of the guiding means.

The size of the last mentioned hole is determing the deflection degree of the piston rod, together with how much the construction of the piston is allowing it. If the piston rod is rigidly fastened to the piston, the construction of the piston determines the deflection degree. If e.g. a ball joint is applied between the piston and the piston rod, the deflection degree is only determined by the guiding means. In a nineth aspect, in order to allow a deflection of the piston rod in relation to the longitudinal centre axis of the rest of the combination, the contact surface of the guiding means may be circular line, e.g. by a convex cross-sectional inner wall of the hole in the guiding means. In a tenth aspect, the piston may be rounded off, so as to comply to the movement of the piston rod, or the connection of the piston to the piston rod may be flexible, turnable.

In the eleventh aspect, the invention relates to a combination of a piston and a chamber, wherein:

- the centre line of the portions of the handle, positioned opposite the centre axis of the combination have an in between angle different from 180°.

The centre lines of the hands of a user when operating a handle of a pump have different positions, depending on how the handle is beying gripped by the hand(s).

In the case oi classic floor pumps, with cylinders with circular cross sections of constant size, high working forces may occur. If relatively high forces are to be transferred from the arm of the user through the hand, connected to this arm, the hand will be best positioned in relation to the arm, when no force moments would arise. This is obtained if the longitudinal axis of the arm goes through the center point of the axis of a portion of the handle, the handle gripped by the hand, connected to the arm.

Due to the relative big size of the force, the grip of the hand on the handle ought to be firm - this may be done by a hand curve like an open fist: the design of the handle may comprise a portion which has circular cross sections. The sizes of the sections may vary, depending on the distance to the centre axis of the piston chamber combination.

A preferred angle between the portions of the handle may in a plane perpendicular the centre axis of the piston-chamber combination be 180°. However, it may also be different from 180°. Additionally may the angle be in a plane which comprises said centre axis less than 180°. In order to avoid the hands from gliding from these protions, stops may be provided for - these may also be used for the force transfer. The other options, 180° and more than 180° may of course also occur.

In the case of innovative floor pumps with a chamber with transversal cross sections of varying sizes between two positions of the chamber in a longitudinal direction, the forces may be low. If relatively low forces are to be transferred from an arm of the user through a hand, connected to said arm, the hand may be positioned in relation to the arm, so that a certain force moment may arise. The contact area is that of an open hand. The handle may be designed with a cross section bounded by the curve of e.g. an ellipse. The axis perpendicular the centre axis of the piston-chamber combination may be larger than the axis parallel to said axis.

Preferred angles between the two portions of the handle in a plane perpendicular to the centre axis of the piston-chamber combination may be bit less than bit bigger (best!) than 180°. These positions of the portions of the handle comply to the rest position(s) of the hand(s). Both positions may be obtained by one handle design, if the handle may be able to turn around the centre axis of the piston-chamber combination.

In order to avoid the existance of a force moment, a line through the centres of both portions of the handle in a plane perpendicular the centre axis of the piston-chamber combination cut the last mentioned axis.

In a plane which comprises the centre axis of the piston-chamber combination the angle may be 180° or less, or different than that.

The conical shape of the cylinder may provide a substantial reduction of the size of the working force. By a special arrangement is the shape of the conical cylinder in the longitudinal direction of the chamber formed in such a way, that the force on the handle remains constant during the stroke. This force may be altered when a valve is opening late, e.g. due to the fact that the valve piston is sticking on the valve seed, or that there be dynamic frictions, e.g. due to small sizes of cross sections of channels - thus by forces originated by other sources than the shape of the chamber. Additionally may the friction of the piston to the wall of the chamber alter during the stroke, due to a change in size of the contact area. The shape of the cylinder shown in the longitudinal direction in all relevant drawings of this patent application is made in the above mentioned way while the transversal cross-sections of the conical cylinder are circular - also this is shown in relevant drawings. The limitation to the shape is the smallest size of the piston.

Thus, 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.

In the situation where the pump is adapted for standing on the floor and the piston/engaging means to compress fluid, such as air, by being forced downwards, the largest force may, economically, be provided at the lowest position of the piston/engaging means/handle. Thus, in the first situation, this means that the highest pressure is provided there. In the second situation, this merely means that the largest area and thereby the largest volume is seen at the lowest position. However, due to the fact that a pressure exceeding that in the e.g. tyre is required in order to open the valve of the tyre, 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 tire (See Fig. 2B).

Also, the invention relates to a shock absorber comprising: a combination according to any of the combination aspects,

The absorber may further comprise a fluid entrance connected to the chamber and comprising a valve means.

Also, the absorber may comprise a fluid exit connected to the chamber and comprising a valve means.

Finally, the invention also 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.

Additionally, the actuator may comprise means for biasing the piston toward the first or second longitudinal position. 19597-1 SPECIFICALLY PREFERRED EMBODIMENTS

According to an embodiment of the invention, there is provided 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 wall at least between a first longitudinal position and a second longitudinal position of the chamber, wherein the combination is flexibly fastened to a basis for engaging the combination to a rigid surface, the combination being movable relatively to said surface wherein the combination is flexibly fastened to the basis by means of an elastically flexible bushing. Preferably is the elastically flexible bushing mounted in a hole in the basis and the cylinder is mounted in a hole in the bushing.

Preferably is the bushing provided with a groove cooperating with a corresponding protrusion on the cylinder.

Preferably is the bushing provided with a protrusion cooperating with a corresponding groove on the cylinder.

Preferably comprises the bushing a protrusion connected to the top of the basis.

Preferably is the wall thickness of the bushing bigger than the wall thickness of the chamber.

Preferably is the basis provided with three engaging surfaces for engaging a rigid surface.

Preferably has the chamber cross-sections of different cross-sectional areas and different circumferential lengths at the first and second longitudinal positions, and continuously differing cross- sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longitudinal position, wherein the piston means can change dimensions thereby providing for different cross-sectional areas and circumferential lengths of the piston means adapting the same to said different cross-sectional areas and different circumferential lengths of the chamber during the relative movements of the piston means between the first and second longitudinal positions through said intermediate longitudinal positions of the chamber.

Preferably has the chamber cross-sections of different cross-sectional areas and equal circumferential lengths at the first and second longitudinal positions, and continuously differing cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longitudinal position, wherein the piston can change dimensions thereby providing for different cross-sectional areas and circumferential lengths of the piston adapting the same to said different cross-sectional areas and equal circumferential lengths of the chamber during the relative movements of the piston means between the first and second longitudinal positions through said intermediate longitudinal positions of the chamber. Preferably is the piston-chamber combination a pump, comprising a means for engaging the piston from a position outside the chamber, and wherein a fluid exit and a fluid entrance comprising a valve means are connected to the chamber.

Preferably is the piston-chamber combination a shock absorber comprising means for engaging the piston from a position outside the chamber, wherein the engaging means have an outer position where the piston is at the first longitudinal position of the chamber, and an inner position where the piston is at the second longitudinal position, wherein the chamber and piston form a sealed cavity comprising a fluid, which is compressed when the piston moves from the first to the second longitudinal position. Preferably is the piston-chamber combination an actuator comprising means for engaging the piston from a position outside the chamber, and means for introducing fluid into the chamber in order to displace the piston between the first and second longitudinal position.

19597-2 SPECIFICALLY PREFERRED EMBODIMENTS

According to an embodiment of the invention, there is provided a piston-chamber combination comprising an elongate chamber which is bounded by an inner chamber wall, and which comprises a piston means in said chamber to be sealingly movable relative to said chamber wall at least between a first longitudinal position and a second longitudinal position of the chamber, said combination engaging a rigid surface, where the combination comprises a piston rod running through a cap capping the chamber, wherein the piston rod is guided by a guiding means movably connected to the cap.

Preferably is the guiding means a washer with an opening fitting around the piston rod, the washer being held within the cap between two surfaces and wherein a flexible O-ring is held within the cap in a space between the surfaces and the guiding means, wherein the cross sectional area of the space is bigger than the cross-sectional area of the O-ring.

Preferably comprises said guiding means a convex guiding surface guiding the piston rod.

Preferably is the piston rounded off at the connection with the wall of the chamber.

Preferably is the connection of the piston rod to the piston (44) flexible.

Preferably is the piston-chamber combination is a pump, comprising a means for engaging the piston from a position outside the chamber, and wherein a fluid exit and a fluid entrance comprising a valve means are connected to the chamber.

Preferably has the chamber cross-sections of different cross-sectional areas and different circumferential lengths at the first and second longitudinal positions, and continuously differing cross- sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longitudinal position, wherein the piston means can change dimensions thereby providing for different cross-sectional areas and circumferential lengths of the piston means adapting the same to said different cross-sectional areas and different circumferential lengths of the chamber during the relative movements of the piston means between the first and second longimdinal positions through said intermediate longitudinal positions of the chamber. Preferably has the chamber cross-sections of different cross-sectional areas and equal circumferential lengths at the first and second longitudinal positions, and at least substantially continuously differing cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longitudinal position, wherein the piston can change dimensions thereby providing for different cross-sectional areas and circumferential lengths of the piston adapting the same to said different cross- sectional areas and equal circumferential lengths of the chamber during the relative movements of the piston means between the first and second longitudinal positions through said intermediate longitudinal positions of the chamber.

19627 BRIEF DESCRIPTION OF THE DRAWINGS

In the following, preferred embodiments of the invention will be described with reference to the drawings wherein:

Fig. 1A 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. 1 B shows an enlargement of the piston of Fig. 1 A at the beginning of a stroke.

Fig. 1 C shows an enlargement of the piston of Fig. 1 A at the end of a stroke.

Fig. 2A 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. 2B shows an enlargement of the piston of Fig. 2A at the beginning of a stroke.

Fig. 2C shows an enlargement of the piston of Fig. 2A at the end of a stroke.

Fig. 3A shows a longitudinal cross-section of a chamber with fixed different areas of the transversal cross-sections and a third embodiment of the piston comprising a fiber reinforcement (no 'Trellis Effect') with radially-axially changing dimensions during the stroke - the piston

arrangement is shown at the beginning, and at the end of a stroke, where it has its production size.

Fig. 3B shows an enlargement of the piston of Fig. 3 A at the beginning of a stroke.

Fig. 3C shows an enlargement of the piston of Fig. 3 A at the end of a stroke.

Fig. 3D shows a top view of the piston of Fig. 3A 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. 3E shows a top view of the piston of Fig. 3A with a reinforcement in the skin in planes partly through the central axis and partly outside the central axis - left: at the first longitudinal position, right: at the second longitudinal position. Fig. 4 shows a non-moving expandable piston inside a chamber with walls, which are parallel to the centre axis, while there are no pressure differences in the chamber between both sides of said piston.

Fig. 5A shows the piston of Fig. 4, instantaneously non-moving inside a chamber with a conical shaped wall, where the piston is beginning to expand - the movable cab is moving toward the non-movable cab.

Fig. 5B shows the piston of Fig. 5 A, instanteneously non-moving, and thereby expanding, so that the contact area of the piston wall with the wall of the chamber increases at second longitudinal positions of said contact area - the movable cab is non-moving.

Fig. 5C shows the piston of Fig. 5B, instanteneously non-moving, and thereby expanding, so that the contact area of the piston wall with the wall of the chamber decreases at second longitudinal positions of said contact area, while the contact area of the piston wall with the wall of the chamber increases at first longitudinal positions of said contact area - the movable cab is non-moving.

Fig. 5D shows the piston of Fig. 5C, where the non-movable cap is instanteneously beginning to move from second to first longitudinal positions, thereby moving the piston in the same direction.

Fig. 5E shows the piston of Fig. 5D, where the movement of the piston is decreasing due to a increasing contact area.

Fig. 6A shows an expandable piston moving in a closed cone shaped chamber.

Fig. 6B shows an expandable piston moving in a closed cone shaped chamber, where said chamber on both sides of the piston is communicating with the surrounding's atmosphere.

Fig. 6C shows an expandable piston moving in a closed cone shaped chamber, where said chamber on both sides of the piston is communicating with each other through a closed channel outside said chamber.

Fig. 6D shows an expandable piston moving in a closed cone shaped chamber, where said chamber on both sides of the piston is communicating with each other through a closed channel inside said piston.

Fig. 6E shows an expandable piston moving in a closed cone shaped chamber, where said chamber on both sides of the piston is communicating with each other through a channel between the chamber wall and the piston wall

Fig. 6F shows the expandable piston of Fig. 6E having a duct in the contact surface of the wall of the piston and the wall of the chamber.

Fig. 6G shows the transversal cross-section of the piston rod of Fig. 6F and the view on the actuator piston from a 1^st longitudinal position.

Fig. 7A shows an enlargement of the piston of Fig. 1 A at the end of a stroke, pressurized, but non-moving, due to the wall being parallel to the centre axis.

Fig. 7B shows the piston of Fig. 7A, at a point where the centre of the wall of the piston has a positive angle in relation to the centre axis, so that the container is moving towards a first position.

Fig. 7D 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. 7E shows the pattern of Fig. 6D when the wall of the container has been expanded

Fig. 7F 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. 7G shows the reinforcement matrix of Fig 7F,

which has been expanded

Fig. 8 shows a combination where the piston is moving

in a chamber and around a taper wall

Fig. 9A shows a longitudinal cross-section of a chamber with fixed different areas of the transversal cross-sections 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 beginning, and at the end of a stroke where it has its production size.

Fig. 9B shows an enlargement of the piston of Fig. 9A at the beginning of a stroke.

Fig. 9C shows an enlargement of the piston of Fig-. 9A at the end of a stroke.

Fig. 9D shows the piston of Fig 9A just entering a conical part of the chamber.

shows a piston-chamber combination where a pressurized ellipso^'ide shaped piston is moving from a second longitudinal position to a first longitudinal position, enlarging the internal volume of said piston, the enclosed space having a fixed volume, thereby reducing the internal pressure of said piston, the piston may change its shape into a sphere - the dashed lines at both ends show the outer contour of said piston, where the chamber has a wall parallel to the centre axis of said chamber, in the - middle the size of said piston compared to where same size of said piston in Fig. 10B occurs, thereby showing that the piston in Fig. 10B may engagingly be connected to the wall of said chamber, while in Fig.1 OA this is sealingly connected.

shows the piston-chamber combination of Fig.1 OA where the internal pressure of the piston additionally has been decreased by changing the volume of the enclosed space, at a furthest first longitudinal position or during its return to the second longitunal position, thereby changing the size of said piston, adapting it contineously to the size of the chamber, in order to avoid jamming.

shows a piston-chamber combination as that of Fig. ΙΟΑ,Β, but where the internal pressure of the piston alternatively has been decreased by removing fluid from the enclosed space, at a furthest first longitudinal position or during its return to the second longitudinal position, thereby changing the size of said piston, adapting it continuously to the size of the chamber, in order to avoid jamming.

shows the process of Fig.1 OA, when the piston is a sphere type, as produced at a second longitudinal position.

shows the process of Fig. 10B, when the piston is a sphere type, as produced at a second longitudinal position.

shows the process of Fig. IOC, when the piston is a sphere type, as produced at a second longitudinal position. shows the process of Fig. 10A, with the exception that the enclosed space has a decreasing size during the moving from the 2^nd to the 1^st longitudinal position, so that the use of the pressurized medium per stroke is being reduced.

shows the comparable process of that of Fig. 10B.

shows the comparable process of that of Fig. IOC.

shows the process of Fig. 10D, with the exception that the enclosed space has a decreasing size during the moving from the 2^nd to the 1^st longitudinal position, so that the use of the pressurized medium per stroke is being reduced.

shows the comparable process of that of Fig. 10E.

shows the comparable process of that of Fig. 10F. shows schematically a motor of the configuration of Figs. 12A and 12C? having a propulsion system comprising an expandable inflatable actuator piston rotating in a circular chamber, having a circleround centre axis, around the centre of the centre axle of said motor.

shows schematically a motor of Fig. 13 A, 13B having a propulsion system comprising (e.g) 5 non-moving expandable inflatable actuator pistons, within a rotating circular chamber, said chamber having a centre line which is concentrical to the centre of rotation, comprising four sub-chambers in continuation of each other, having continuing differing transitional cross- sectional area's and circumferences, said chamber is rotating around a main axle through the center of said axle

CONSUMPTION TECHNOLOGY

Fig. 11A shows schematically a motor having a propulsion system comprising an expandable inflatable actuator piston, and a two step piston pumping system, within an elongated chamber having continuing differing cross-sectional area's and circumferences, all assembled on a crankshaft axle, and a pressure storage vessel, and an electric starter motor, the smallest pump and starter motor being energized by among others solar energy.

Fig. 1 IB shows schematically the controlling means and the pressure management for the motor of Fig. 1 1 A.

Fig. l lC shows some worked out mechanical assemblies of the motor of Figs. 11A and

1 IB, where the main cylinder is not moving.

Fig. 1 ID shows the pressure management of the inflatable actuator piston on the joint of the crankshaft and the connecting rod, shown in Fig. 11 C.

Fig. 1 IE shows a detail of the joint of the piston rod and the connecting rod, shown in

Fig. l lC.

Fig. 1 IF shows a detail of the suspension of the crankshaft, and the channel inside said crankshaft, shown in Figs. 11 A and 1 IB.

ENCLOSED SPACE VOLUME TECHNOLOGY

Fig. 11G shows an alternative method of managing the pressure change in the inflatable actuator piston, by changing the volume of the enclosed space through a piston of a second piston-chamber combination, and an additional adjustment of the pressure through a piston of a third piston-chamber combination for managing the speed/power of said motor, without a constant repressuration of the pressure storage vessel, for pressurizing the 2-way actuator for said change of volume of the enclosed space.

Fig. 11H shows the configuration of Fig. 11G, where a constant repressuration of the pressure storage vessel is done by a cascade of pumps, shown in e.g. Fig. 11A.

Fig. I ll shows a partially worked out one cylinder motor, based on the concept shown in Fig. 1 1H, where the velocity controller and the ESVT-pump are being powered by a 2-way actuator, which is powered by a battery; the pump for re-pressurating the pressure storage vessel is being powered by a separate electric motor, powered by a battery - the respective power lines are clearly shown - auxilliarly power sources are according to Figs. 15A,B,C,E,F of which at least one may charging said batteries.

Fig. 11 J shows a partially worked out two cylinder motor, based on Fig. I ll, where each actuator piston-chamber combination has a separate velocity controller and an ESVT-pump - said velocity controllers are communicating with each other.

Fig. 1 1 J left shows a scaled up of the left part of Fig. 1 1 J.

Fig, 11 J right shows a scaled up of the right part of Fig. 11 J.

Fig. 1 IK shows a partially worked out one cylinder motor, based on the concept shown in Fig. 11H, where the ESVT-pump of the actuator piston now is being powered by a crankshaft, the last mentioned being powered by an electric motor, which is powered by a battery - the velocity controller (2 way- actuator) is according the one of Fig. 11H; the pump for re-pressurating the pressure storage vessel is being powered by a separate electric motor, powered by a battery; auxilliarly power sources are according to Figs. 15A,B,C,E,F of which at least one may charging said batteries.

Fig. 11L shows a partially worked out two cylinder motor, based on Fig. UK. One crankshaft is being used for the ESVT-pumps, one for each actuator-piston combination. The velocity controllers, one for each actuator piston are communicating with each other; the pump for re-pressurating the pressure storage vessel is being powered by a separate electric motor, powered by a battery; auxilliarly power sources are according to Figs.

15A,B,C,E,F of which at least one may charging said batteries.

Fig. 11 L left shows a scaled up of the left part of Fig. 11 L.

Fig, 11 L right shows a scaled up of the right part of Fig. 11 L.

Fig. 11M shows a partially worked out one cylinder motor, based on the concept shown in Fig. 11H, where the ESVT-pump for the actuator piston chamber combination now is being powered by a camshaft, said camshaft driven by an electric motor, powered by a battery; the velocity controller is a 2-way actuator, which is communicating with a speeder. The pump for repressurating the pressure storage vessel is being powered by a separate electric motor, powered by a battery; auxilliarly power sources are according to Figs. 15A,B,C,E,F of which at least one may charging said batteries.

Fig. UN shows a partially worked out two cylinder motor, based on Fig. 11M - one camshaft is used for the ESVT-pumps, one for each actuator piston-chamber combination.The velocity controllers, one for each actuator piston, are communicating with each other; the pump for repressurating the pressure storage vessel is being powered by a separate electric motor, powered by a battery; auxilliarly power sources are according to Figs. 15A,B,C,E,F of which at least one may charging said batteries.

Fig. 1 IN left shows a scaled up of the left part of Fig. 1 IN.

Fig, 1 IN right shows a scaled up of the right part of Fig. 1 IN.

Fig. l lo shows a partially worked out one cylinder motor, based on the concept shown in Fig. 1 1 K, where the ESVT-pump of the actuator piston-chamber is being powered by a crankshaft, which is directly driven by the auxilliarly power from a gas (e.g. air) cooled combustion motor, using H₂, derived by the electrolyses of H₂0, said electrolyses powered by a battery; the pump which is re-pressurating the pressure storage vessel is additionally directly driven by said combustion motor; the velocity controller is powered by a 2- way actuator, powered by a battery; the batteruies according to Fig. 15D are being charged by an alternator, which is mounted on the main motor axle. The generated heat of said combustion motor may be used e.g. for warming up the vehicle interior.

Fig. I IP shows a partially worked out two cylinder motor, based on Fig. l lo, where the ESVT-pumps, one for each actuator piston-chamber combination, are being powered by a crankshaft, which is directly driven by the auxilliarly power from a forced liquid cooled combustion motor, using H₂, derived by the electrolyses of H₂0, said electrolyses powered by a battery; the pump pump, which is re-pressurating the pressure storage vessel is directly driven by said combustion motor; the velocity controllers, one for each actuator piston chamber combination are powered by a 2-way actuator, are communicating with each other, and are powered by a battery; the batteries according to Fig. 15D are being charged by an alternator, which is mounted on the main motor axle. The generated heat of said combustion motor may be used e.g. for warming up the vehicle interior.

Fig. 1 IP left shows a scaled up of the left part of Fig. 1 IP.

Fig, 1 IP right shows a scaled up of the right part of Fig. 1 IP.

Fig. HQ shows a partially worked out one cylinder motor, based on the concept shown in Fig. UK, where the ESVT-pump of the actuator piston-chamber combination are being powered by a camshaft which is directly driven by the auxilliarly power from a forced gas (e.g. air) cooled combustion motor, using H₂, derived by the electrolyses of H₂0, said electrolyses powered by a battery; the pump, which is re-pressurating the pressure storage vessel is directly driven by said combustion motor; the velocity controller is powered by a 2-way actuator, powered by a battery; the batteries according to Fig. 15D are being charged by an alternator, which is mounted on the main motor axle. The generated heat of said combustion motor may be used e.g. for warming up the vehicle interior.

Fig. 11R shows a partially worked out two cylinder motor, based on Fig. HQ - where the ESVT-pumps, one for each actuator piston-chamber combination, are being powered by a camshaft, which is directly driven by the auxiliary power from a gas (e.g. air) forced cooled combustion motor, using H₂, derived by the electrolyses of H₂0, said electrolyses powered by a battery; the pump which is re-pressurating the pressure storage vessel is directly driven by said combustion motor; the velocity controllers, one for each actuator piston-chamber combination are powered by a 2-way actuator, are communicating with each other, and are powered by a battery; the batteries according to Fig. 15D are being charged by an alternator, which is mounted on the main motor axle. The generated heat of said combustion motor may be used e.g. for warming up the vehicle interior. Fig. 11R left shows a scaled up of the left part of Fig. 11 R.

Fig. 11R right shows a scaled up of the right part of Fig. 11R.

Fig. US shows a detail of the joint of the base of the piston-chamber combination

1061 of Figs. 1 II - 11R with the main axle of the motor.

Fig. 1 IT shows a detail of the joint of the connecting rod of the actuator piston and the crankshaft on the main axle of the motor according to Figs. 1 II - 1 1R.

Fig. 11U shows a detail of the joint of the base of the piston-chamber combination

1060 of Figs. 111 - 1 1R with the main axle of the motor.

Fig. 1 IV shows the mechanism driving a pump of Figs. 11H - 11R, and its base.

Fig. 11W shows the connecting joint between the two crankshafts of the 2-cylinder motor according to Figs. 11 J, 11L, 1 IN, 1 IP, 11R.

Fig. 11 W shows an improved sealing between the crankshafts of Fig. 11 W.

Fig. 1 IX shows the connecting joint between the two crankshafts of a 2-cylinder motor where the channels of each crankshaft are being separated.

Fig. 1 IX' shows an improved sealing between the crankshafts of Fig. 1 IX

CONSUMPTION TECHNOLOGY shows schematically a motor having a propulsion system comprising an expandable inflatable actuator piston rotating in a circular chamber, and a two step piston pumping system, within an elongated chamber having continuing differing transitional cross-sectional area's and circumferences, all assembled on a crankshaft axle, and a pressure storage vessel, and an electric starter motor, the smallest pump and starter motor being energized by solar energy, including control means.

shows schematically a motor of Fig. 12A having a propulsion system comprising an expandable inflatable actuator piston moving within a non- moving chamber, having a centre line which is concentrically the centre of rotation, comprising four sub-chambers in continuation of each other, having continuing differing transitional cross-sectional area's and circumferences, shows schematically the controlling means and pressure management for the motor of Fig. 12B, where the change of the pressure in the actuator piston is controlled by adding to and removing fluid from the actuator piston

ENCLOSED SPACE VOLUME TECHNOLOGY

Fig. 12D shows schematically the controlling means and pressure management for the motor of Fig. 12B, where the change of the pressure in the actuator piston is controlled by changing the volume of the enclosed space of the actuator piston.

CONSUMPTION TECHNOLOGY shows schematically a motor having a propulsion system comprising more than one non-moving expandable inflatable actuator pistons in a rotating chamber, said chamber having a centre line which is concentrically the centre of rotation, and a two step piston pumping system, within an elongated chamber having continuing- differing transitional cross-sectional area's and circumferences, all assembled on a crankshaft axle, and a pressure storage vessel, and an electric starter motor, the smallest pump and starter motor being energized by solar energy.

shows the motor of Fig. 13 A, wherein the piston pumps of the two step piston pumping system have been exchanged by rotational pumps, mounted on the main axle of the motor.

shows schematically a motor of Fig. 13A, 13B having a propulsion system comprising non-moving expandable inflatable actuator pistons, within a rotating chamber, said chamber having a centre line which is concentrically the centre of rotation, comprising four sub-chambers in continuation of each other, having continuing differing transitional cross-sectional area's and circumferences, said chamber is rotating around an axle through the center of said chamber.

shows schematically the suspension of the motor of Fig. 13 A, 13B, incl. a drive belt.

shows schematically the controlling means and pressure management for the motor of Fig. 13A,13B incl. a storage pressure vessel, where the continuously changing internal pressures of said actuator pistons are determined by a separate piston-chamber combination for each of said actuator pistons, computer controlled. ENCLOSED SPACE VOLUME TECHNOLOGY

Fig. 13F shows the pressure management of the inflatable pistons of Fig. 13C, according to the principle of Fig. 1 IF, where each actuator piston is managed by two piston-chamber combinations - one for the continuously changing pressure and one for the adjustment of the pressure level for adjusting the speed/power of the motor.

Fig. 13 G shows the pressuration system for the configuration of Fig. 13F.

ENCLOSED SPACE VOLUME TECHNOLOGY shows the several stages of an actuator piston, around which a circular chamber is running, and what is necessary to change the inside pressure of said actuator piston, by changing the volume under a pump piston of a connected chamber. shows the configuration of Fig. 14A, where a cam- wheel which is connected to the piston rod of the pump piston, is communicating with a cam of an appropriate profile.

shows

shows a moving circular chamber according to Fig. 13 A, where the pressure in actuator pistons is being defined by the pressure in a piston-chamber combination which has a cam-wheel communicating with the piston of said piston-chamber combination, said cam-wheel is running over a main axle, which is comprising a cam with a certain profile.

shows a rim with its suspension, in which the configuration of Fig. 14D has been built in, together with an auxilliarly motor, shown as an electric motor, which is turning said cam profile; communicating to a channel comprising the enclosed space of said actuator piston is a pressure controller according to the configuration of Fig. 16 ("drive by wire") , which is communicating with a remotely speeder.

shows an enlarged detail of the cross-section of said piston in said circular chamber of Fig. 14E, when the piston is at a first circular position.

shows an enlarged detail of the cross-section of said piston in said circular chamber of Fig. 14G, when the piston is at a second circular position.

shows the configuration of Fig. 14E, wherein between the rim of the wheel and said circular chamber has been built in a gearbox, e.g. of the type of a planet gear. SHORT DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 141 shows that part of the pressure management system which is controlling the speed of the motors, e.g. on which a wheel / propeller has been mounted, when said wheels / propellers of a vehicle have different speeds e.g. for wheels of a car, while turning around a corner.

AUXILLIARLY POWER SOURCES shows a H₂-fuel cell as electrical power source for repressuration pump(s) for pressurizing the pressure storage vessel, the necessary components and the power lines.

shows a combustion motor, using H₂ as power source, which has been generated by electrolyses of conductive- water - the axle of said combustible is driving an alternator which is charging a battery — the battery let an electric motor run, which is communicating with (a) pump(s), for repressuration of the pressure storage vessel.

shows a combustion motor, using H₂ as power source, which has been generated by electrolyses of conductive water - the axle of said combustible is directly communicating with (a) pump(s) through (a) crankshaft, for repressuration of the pressure storage vessel.

shows a combustion motor, using ¾ as power source, which has been generated by electrolyses of conductive water - the axle of said combustible is directly communicating with (a) rotational pump(s), for repressuration of the pressure storage vessel.

shows a capacitator, which is electrically charged, and which is the power source for electrical motor(s), which are communicating with (a) pump(s) for repressuration of the pressure storage vessel.

ESVT - CRANKSHAFT DESIGN - MULTIPLE USE OF COMPONENTS

Fig. 16A shows a scaled up 2- way actuator of the Figs. 11G-R. Fig. 16B shows a pre-study of the 2- way actuator of Fig. 16A.

ESVT - CRANKSHAFT DESIGN - MULTIPLE USE OF COMPONENTS

Fig. 17A shows schematically the two strokes of an actuator piston according to Figs.

ΙΟΑ,Β of a one cylinder motor, where the stroke from a 2^nd to a 1^st longitudinal position is the power stroke, and the stroke from the 1^st to the 2^nd longitudinal position the (powerless) return stroke.

Fig. 17B shows a two cylinder motor ("A" and "B") with strokes according to Fig.

17A, whereby the crankshaft (comprising of two sub-crankshafts) is designed, so that the power strokes of each cylinder are moving in opposite

(180°) direction.

Fig. 17C shows a two cylinder motor according to Fig.11 R, whereby the combustion motor here is forced liquid cooled, whereby one of the ESVT-pumps has been exchanged by an inlet/outlet for one sub-crankshaft, which is communicating with the ESVT-pump for the other sub-crankshaft, and where said communication is controlled by valve actuators according to Fig. 210E, of which motion are initiated by cams of a camshaft, said camshaft being driven by said combustible motor, and, such that the beginning of the power stroke of the left cylinder, is synchronized with the beginning of the return stroke of the right cylinder; the second enclosed space of one sub-crankshaft has been separated from the third enclosed space of the other sub-crankshaft.

Fig. 17C 1. shows an enlargement of Fig. 17C left and a diagram of the in-between relationship of the connection rods of both actuator pistons.

Fig. 17C r. shows an enlargement of Fig. 17C right.

Fig. 17D shows the middle of the power stroke of the left cylinder, and the middle of the return stroke of the right cylinder of the motor according to Fig. 17C.

Fig. 17D I. shows an enlargement of Fig. 17D left and a diagram of the in-between relationship of the connection rods of both actuator pistons.

Fig. 17D r. shows an enlargement of Fig. 17D right. Fig. 17E shows the end of the power stroke of the left cylinder and the end of the return stroke of the right cylinder of the motor according to Fig. 17D.

Fig. 17E 1. shows an enlargement of Fig. 17E left and a diagram of the in-between relationship of the connection rods of both actuator pistons.

Fig. 17E r. shows an enlargement of Fig. 17E right.

Fig. 17F shows the beginning of the return stroke of the left cylinder and the beginning of the power stroke of the right cylinder of the motor according to Fig. 17E.

Fig. 17F 1. shows an enlargement of Fig. 17F left and a diagram of the in-between relationship of the connection rods of both actuator pistons.

Fig. 17F r. shows an enlargement of Fig. 17F right.

Fig. 17G shows the middle of the return stroke of the left cylinder and the middle of the power stroke of the right cylinder of the motor according to Fig. 17F.

Fig. 17G 1. shows an enlagement of Fig. 17G left and a diagram of the in-between relationship of the connection rods of both actuator pistons.

Fig. 17G r. shows an enlagement of Fig. 17G right. Fig. 17H shows the end of the return stroke of the left cylinder and the end of the power stroke of the right cylinder of the motor according to Fig. 17G.

Fig. 17H 1. shows an enlagement of Fig. 17H left and a diagram of the in-between relationship of the connection rods of both actuator pistons.

Fig. 17H r. shows an enlagement of Fig. 17H right.

ESVT- CRANKSHAFT DESIGN - MULTIPLE USE OF COMPONENTS

Fig. 18A shows a two cylinder motor ("A" and "B") with strokes according to

Fig.l7A, whereby the crankshaft (comprising of two sub crankshafts) is designed, so that the power strokes of each actuator pistons are moving in the same (0°) direction.

Fig. 18A 1. shows an enlargement of Fig. 18A left and a diagram of the in-between relationship of the connection rods of both actuator pistons.

Fig. 18A r. shows an enlargement of Fig. 18 A right.

Fig. 18B shows a simple configuration of a two cylinder motor according to Fig.l7C, whereby the combustion motor here is forced liquid cooled, comprising one ESVT-pump serving both actuator pistons has, the second enclosed space of one sub-crankshaft is communicating with the third enclosed space of the other sub-crankshaft,

such that the beginning of the power stroke of the left cylinder, is synchronized with the beginning of the power stroke of the right cylinder.

Fig. 18B 1. shows an enlargement of Fig. 18B left and a diagram of the in-between relationship of the connection rods of both actuator pistons.

Fig. 18B r. shows an enlargement of Fig. 18B right.

Fig. 18C shows the middle of the power strokes of the left and the right cylinder of the motor according to Fig. 18B.

Fig. 18C 1. shows an enlargement of Fig. 18C left and a diagram of the in-between relationship of the connection rods of both actuator pistons.

Fig. 18C r. shows an enlargement of Fig. 18C right.

Fig. 18D shows the end of the power strokes of the left and the right cylinder of the motor according to Fig. 18C.

Fig. 18D 1. shows an enlargement of Fig. 18D left and a diagram of the in-between relationship of the connection rods of both actuator pistons. Fig. 18D r. shows an enlargement of Fig. 18D right.

Fig. 18E shows the beginning of the return stroke of the left and the right cylinder of the motor according to Fig. 18D.

Fig. 18E 1. shows an enlargement of Fig. 18E left and a diagram of the in-between relationship of the connection rods of both actuator pistons.

Fig. 18E r. shows an enlargement of Fig. 18E right. Fig. 18F shows the middle of the return stroke of the left and the right cylinder of the motor according to Fig. 18E.

Fig. 18F 1. shows an enlargement of Fig. 18F left and a diagram of the in-between

relationship of the connection rods of both actuator pistons.

Fig. 18F r. shows an enlargement of Fig. 18F right.

Fig. 18G shows the end of the return stroke of the left and the right cylinder of the motor according to Fig. 18F.

Fig. 18G 1. shows an enlargement of Fig. 18G left and a diagram of the in-between relationship of the connection rods of both actuator pistons.

Fig. 18G r. shows an enlargement of Fig. 18G right.

CT - CRANKSHAFT DESIGN - MULTIPLE USE OF COMPONENTS

Fig. 19A shows a one cylinder motor, based on Figs. 11B, 11C, where some parts have been worked out further - the auxilliarly power source is a combustion motor, which is burning H₂, derived from electrolyses of H₂0.

Fig. 19B shows a two cylinder motor, based on Fig." 19 A, where the two cylinders have been mirrowedly positioned to the center line of the connection, so that the 3 ^rd enclosed spaces (exits) are communicating with each other through the connection of the two sub-crankshafts, while the 2^nd enclosed spaces (inlets) are communicating outside said crankshaft with each other (with a check valve), and where the crankshaft (comprising of two sub-crankshafts) is designed, so that the power strokes of each actuator piston are moving simultaneously in the same (0°) direction (synchrone), according to the principle of Fig. 18 A.

Fig. 19B 1. shows an enlargement of Fig. 19B left.

Fig. 19B r. shows an enlargement of Fig. 19B right.

Fig. 19C shows a two cylinder motor, based on Fig. 19A, where the comparable enclosed spaces (here the 3 ^rd enclosed spaces) have been connected to each other through the sub-crankshafts, while the 2^nd enclosed spaces have been brought externally together (with a check valve), and where the whereby the crankshaft (comprising of two sub-crankshafts) is designed, so that the power strokes of each actuator pistons are moving in the same (180°) direction (asynchrone), according to the principle of Fig. 18 A.

Fig. 19C 1. shows an enlargement of Fig. 19C left.

Fig. 19C r. shows an enlargement of Fig. 19C right. 19620 BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 21 A shows a longitudinal cross-section of a conical shaped

chamber with constant

maximum work force characteristics of a pump showing the common (pressure) borders, and the convex and conical shapes of - the sides of the

longitudinal cross-sectional sections between said borders

Fig. 21 B shows the chamber of Fig. 21 A ( 10 Bar overpressure),

and (dashed) the

shape of another chamber (16 Bar overpressure), for the

same chamber

length.

Fig. 22 shows a longitudinal cross-section of a conical shaped

chamber of Fig. 21

showing an expansion chamber as continuation of said chamber. Fig. 23 shows an advanced conical shaped chamber with constant

maximum work

force characteristics of a pump showing the specific

internal concave

transition from the internal conically shaped part of the chamber to the straight inside at second longitudinal positions, which is

parallel to the centre

axis of the chamber.

Fig. 24 shows an expandable deformable piston, which will not

move by itself from

a second longitudinal position to a first longitudinal

position, because the

internal wall of the chamber of Fig. 23 is parallel to the

centre axis.

Fig. 25 shows a chamber of a constant force type, with a hose nipple as exit, which is connected to a hose. 19630 BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 30A shows the circular chamber of Fig. 12B, where a piston is moving in a non-moving chamber.

Fig. 30B shows the circular chamber of Figs. 13C and 14D where the piston is not moving, but the chamber. Here is the design of the circular chamber and the sub-chambers identical with the design of Fig. 3 OA.

Fig. 31 A shows the Fig. 14D, where the section X-X has shown.

Fig. 3 IB shows an scaled up detail of section X-X of the chamber of Fig. 31 A.

MATHEMATICAL DESCRIPTION OF THE CIRCULAR CHAMBER AND A PISTON

Fig. 32A shows the ^'wall of the chamber and the orthogonal plane to the base circle intersects in a circle whose center is at the bas circle.

Fig. 32B a section of the boundary of the piston.

Fig. 32C shows the cap geometri - for area and internal volume of the cap we need need values of a and h only - see formulas (2.1) and 2.2) - the radius of the virtual sphere is given in (2.3).

Fig. 32D shows the piston with end caps.

Fig. 32E shows the piston with end caps inside a transparent Fermi tube chamber.

Fig. 32F shows the pure contact area between the piston and the chamber, visible inside the transparent chamber wall.

Fig. 32G shows the contact area between the piston and the chamber.

Fig. 32H shows a section of the chamber wall - the chamber reaction force is marked by gray - the total force on the section is orthogonal to the chamber wall - for the section is the value of the force proportional to the (variable) longitudinal length of the shown section and to the internal pressure of the piston.

Fig. 321 shows the section of Fig. 32H, with an additional section in order to provide an open view. Fig. 32J shows Fig. 32H, and the red vector is the component of the gray force in the longitudinal direction.

Fig. 32K shows Fig. 32J, with an additional section in order to provide an open view.

Fig. 32L shows Fig. 32J, where the actual sliding force along the wall is shown in blue - it is obtained by projecting the red vector orthogonally to the chamber wall.

Fig. 32M shows Fig. 32L, with an additional section in order to provide an open view.

19640 BRIEF DESCRIPTION OF THE DRAWINGS

In the following, preferred embodiments of the invention will be described with references to the drawings wherein: shows a longitudinal cross-section of a pump with a piston comprising support means, an O-ring and a flexible impervious layer, the last mentioned supported by a foamy at a first longitudinal position.

shows a detail of the suspension of the support means, O-ring and the flexible impervious layer, vulcanised together.

shows a longitudinal cross-section of the piston of Fig. 40A at a second longitudinal position.

shows top view of the piston of Fig. 40A and a cross-section of the chamber from a first longitudinal position.

shows a detail of the suspension on the support means of the O-ring and the lying spring of the piston of Fig. 40A.

shows a transversal cross section of the chamber with the piston of Fig. 40A at a second longitudinal position.

shows a bottom view of the piston of Fig. 40A, and cross-section of the chamber at a first longitudinal position, showing the spiral reinfor- ment of the impervious sheet.

shows a bottom view of the piston of Fig. 40A, and cross-section of the chamber at a first longitudinal position, showing the spiral reinfor- ments of the impervious sheet.

shows a longitudinal cross-section of a piston comprising support means, an O-ring and a flexible impervious layer, the last mentioned at a centain angle with the centre axis of the chamber, at a first longitudinal position.

shows a longitudinal cross-section of the piston of Fig. 42A at a second longitudinal position. 19650 BRIEF DESCRIPTRION OF THE DRAWINGS

Fig. 50. shows the top view of a foam piston, specifically the suspension of reinforcement pins.

Fig. 51 shows a longitudinal cross-section A-A of a piston made of a PU foam.

Fig. 52 shows a longitudinal cross-section B-B of the piston of Fig. 50

19650-1 DESCRIPTION OF THE DRAWINGS

Fig. 55 A shows the piston at 1^st longitudinal position of an advanced pump, said piston is comprising metal pins, which are rotatably fastened by magnetic force to a holder plate of a holder, which is mounted on the piston rod.

Fig. 55B shows an enlargement longitudinal cross-section P-P of the holder plate mounted on said holder.

Fig. 55C shows an enlargement of the holder plate on the holder from Fig. 55B.

Fig. 55D is showing an enlargement of the protuberance in a reces between the holder and the holder plate for an improved squeezing of the impervious layer. Fig. 55E shows an alternative solution for the reinforcement and the fastening of the foam to the one shown in Figs. 55A-D.

Fig. 55F shows an enlargement of the holder plate on the holder from Fig. 55E. Fig. 55G shows a solution for an automatic clockwise rotation of the reinforcement pins of the foam when the piston is running towards a 1^st longitudinal position.

Fig. 55H shows an enlargement of the holder plate on the holder from Fig. 55G. 19660 BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 60 shows a longitudinal view and cross-sections of the ends of a container type piston Fig. 61 shows the details of both end of the container type piston of Fig. 60.

Fig. 62 shows the container type piston at the begin and end of a stroke, in a chamber where the force on the piston rod is constant (please see 19620).

19660-2 BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 63 shows the forces from an actuator piston to the wall of a longitudinal chamber.

Fig. 64A shows an ellipsoide type piston in a chamber with a longitudinal centre axis, with a 20° angle.

Fig. 64B shows an ellipsoide type piston in a chamber with a longitudinal centre axis, with a 10° angle.

19680-2 BRIEF DESCRIPTION OF THE DRAWINGS

In the following, preferred embodiments of the invention will be described with reference to the drawings wherein: Fig. 80A shows a chamber of a pump according to section 19620, with a piston according to section 19680 on three different longitudinal positions, said piston wall is comprising a separate rotatable part, which adapt to the slope of the wall of said chamber, and of which surfaces are sealingly connected to the wall of the chamber and said piston wall.

Fig. 80B shows a scaled up detail of said contact area's when said piston is in a first longitudinal position.

Fig. 80C shows a scaled up detail of the contact area's when said piston is in a second longitudinal position.

Fig. 80D shows the separate part when the piston is in a second longitudinal position.

Fig. 80E shows an alternative sphere shape of the separate part of that shown in

Figs. 80A-C.

Fig. 80F shows an alternative halfround shape of the separate part of that shown in Figs. 80A-C, which has been vulcanized on a (scaled up) piston according to section 19660, when said piston is in a second longitudinal position.

Fig. 80G shows the piston according to Fig. 80F, where the separate part is positioned under a line through the longitudinal middle point of the flexible wall of said piston.

Fig. 80H shows the piston according to Fig. 80C where the separate part is positioned under a line through the longitudinal middle point of the flexible wall of said piston.

Fig. 801 shows the piston of Fig. 80J at a second longitudinal position of the chamber according to section 19620.

Fig. 80J shows an enlargment of the piston of Fig. 801, as produced.

Fig. 81 A shows a chamber of a pump according to section 19620, with an inflatable piston according to section 19680 on three different longitudinal positions, said piston wall is comprising two separate rotatable parts, which adapt to the slope of the wall of said chamber, and of which surfaces are sealingly connected to the wall of the chamber and said piston wall.

shows a scaled up detail of said contact area's when said piston is in a first longitudinal position.

shows a scaled up detail of said contact area's when said piston is positioned between a first and a second longitudinal position.

shows said (scaled up) piston, which is positioned in a second longitudinal position.

shows a chamber of a pump according to section 19620, with an inflatable piston according to section 19680 on three different longitudinal positions, said piston wall is comprising two parts, having different circumferences, where the biggest is comprising the contact area between the wall of the chamber and the piston wall.

shows a scaled up detail of said contact area when said piston is in a first longitudinal position.

shows a scaled up detail of said contact area when said piston is positioned between a first and a second longitudinal position.

shows the piston of Fig. 82D, comprising a piston rod, uninflated.

shows the piston of Fig. 83A at a first longitudinal position, being inflated.

shows the piston of Fig. 83B, with a clamp in the piston rod, holding the piston in position, when deflated.

shows the piston of Fig. 83C, when a foam is being inserted through the enclosed space of the piston rod.

shows the piston of Fig. 83D, after insertion and hardening of the foam, which has been undamped thereafter.

shows the piston of Fig 83E on a second longitudinal position, having a pressure sensor and a inflation valve. shows the enlargement of the pressure sensor and the inflation valve of the piston of Fig, 83E.

shows the piston of Fig, 83E on a second longitudinal position, with a pressure sensor and a inflation valve of another type than the one shown in Fig. 83F or 83G.

shows the enlargement of the pressure sensor and the inflation valve of the piston of Fig, 83H.

shows the piston of Fig, 83E on a second longitudinal position, with a pressure sensor and a inflation valve of another type than the one shown in Fig. 83F, 83G or 83H.

shows the enlargement of the pressure sensor and the inflation valve of the piston of Fig, 83 J.

shows the piston of Fig. 83H for e.g. small size use, where a pulling spring is giving a expansion force for the piston wall, besides the force derived from the inflatable toroid, which communicate with the enclose space - the pressure side of the pump piston has foam inside, so to keep expanding that part properly under external pressure.

shows an improved piston based on Fig. 84A, which has foam inside the whole piston, communicating through a venting hole to the non- pressurized outside of the piston, and a separate channel assembled on the inside of the piston wall, which is communicating with the enclosed space of said piston.

shows the piston of Fig. 84A, where the low-pressure side of the wall of the piston is a flat cone.

shows a sphere shaped piston on a second and first longitudinal position of a chamber with a separate part on the outer wall as shown in Figs. 80F, 80G, 80J for an ellipsoide type of piston.

shows a sphere shaped piston with a piston wall, said piston wall is comprising two parts, having different circumferences, where the biggest is comprising the contact area between the wall of the chamber and the piston wall (such as shown in Figs. 82A-D for ellipsoide shaped piston types), while the piston is shown on a second and first longitudinal position.

shows a sphere piston with a inflatable toroid as separate part, as shown in Fig. 84B for a ellipsoide shaped piston.

19690-2 - SHORT DESCRIPTION OF PTREFERRED EMBODIMENTS

In the following, preferred embodiments of the invention will be described with reference to the drawing wherein:

A single moving piston in a chamber

Fig. 90A shows a rotating piston in a circular chamber, where the piston is connected to the axle by a connecting rod, said axle and connecting rod are comprising a channel, communicating with each other.

Fig. 90B shows an enlargement of a detail of the assembling of the connection rod and the axle, and the teeth between the axle and the connecting rod.

Fig. 90C shows the enlargement of the connecting rod on which the piston is mounted, based on Fig. 14F, when the piston is positioned at a first circular position.

Fig. 90D shows the enlargement of the connecting rod on which the piston is mounted, based on Fig. 14G, when the piston is positioned at a second circular position. together with CT and/or ESVT-systems

Fig. 90E shows the construction of Fig. 90A where the channel in the axle is communicating with a CT - pressure management system according to Fig. 1 1 A, and Fig. 1 ID for the joint of the connecting rod to the axle.

Fig. 90F shows the construction of Fig. 90A where the channel in the axle is communicating with a ESVT - pressure management system according to Fig. 1 1G, and Fig. 1 IT for the joint of the connecting rod to the axle.

Fig. 90G shows the construction of Fig. 90A where the channel in the axle is communicating with a ESVT - pressure management system according to Fig. I ll, and Fig. 1 IT for the joint of the connecting rod to the axle.

Fig. 90H shows a preferred embodiment based on the construction of Fig. 90G in combination of a camshaft, which is controlling the timing of the ESVT

- system, while the energy comes from a combustion motor, driven by H₂, derived from electrolyses of H₂0.

Multiple moving pistons in a chamber (at the same circular position)

Fig. 901 shows 4 moving pistons in a chamber, of which the space within each piston is communicating with the enclosed space in each connecting rod, which are communicating with the enclosed space of the axle, around which said pistons are moving.

Fig. 90J shows an enlargement of the joint between the connecting rods and the axle of Fig. 901. together with an ESVT-system

Fig. 90 shows the construction of Fig. 901, where the channel in the axle is communicating with an ESYT-pressure management system according to Fig 111, and a joint based on Fig. 1 IT and Fig. 90J. Fig. 90L shows a preferred embodiment of the motor, based on the construction of Fig. 90K in combination of a camshaft, which is controlling the timing of the ESVT - system, while the energy comes from a combustion motor, driven by H_2> derived from electrolyses of H₂0. Single moving chamber around a piston

Fig. 91 A shows a rotating circular chamber, in which a piston is positioned, where the piston is connected to the axle by a connecting rod, said axle and connecting rod are comprising a channel.

Fig. 91B shows an enlargment of a detail of the assembling of the connecting rod and the axle of Fig. 91 A, the bearing between the axle and the connecting rod, and said channels, communicating intermediate with each other - this construction may preferably be combined with a CT- system. the same combinations are possible with the CT and/or ESVT-systems as shown for Figs. 90K-90L (incl.).

Fig. 91 C shows the cross-sections of the hub comprising the channels of the connecting rod and the axle, and a bearing with a hole, and teeth and grooves for securing the position of the non-moving piston.

Fig. 91D shows a cross-sections as designated in Fig. 91C, where the rotation of the bearing is provided by a rotation of the hub of the spokes of said chamber.

Fig. 9 IE shows the cross-section of the hub comprising the channels of the connecting rod and the axle where a reduced axle diameter provides a constant communication between said channels. (FROM 19619-EP)

Multiple rotating pistons in parallel chambers

Fig. 92A shows a 3 -cylinder motor, where the pistons are rotating around a main centre axis - the chambers are interconnected and a gearbox is mounted on said assembly, its main axle is communicating with said main central axle of said pistons - this construction may preferably be combined with an ESVT-system. Fig. 92B shows the 3 cylinder motor of Fig. 92A - on said main axle, on each side of said motor is a variable pitching wheel assembled, which are communicating to comparable pitching wheels on a wheel axle of a vehicle, shown is the low pitch mode (Variomatic^®): low speed - this construction may preferably be combined with an ESVT-system.

Fig. 92C shows the same as Fig. 92B, but where the pitches of said wheels have been reversed: high speed.

Multiple moving chambers transferring the torque to a central axle

Fig.93A shows a 3-cylinder motor, where the chambers are rotating, the torque is being transferred to a main central axle, and an external gearbox is communicating with said axle - this construction may preferably be combined with an ESVT-system.

Fig. 93 B shows an enlargement (4:1) of the left corner of the building up of the central axle of said motor.

207 BRIEF DESCRIPTION OF THE DRAWINGS

The invention is explained in detail below by means of diagrams and drawings. The following is shown in the diagrams or drawings - a transversal cross-section means a cross-section perpendicular to the moving direction of the piston and/or the chamber, while the longitudinal cross-section is the one in the direction of said moving direction:

Fig. 100 shows a so-called indicator diagram of a one-stage single working piston pump with a cylinder and a piston with a fixed diameter.

Fig. 102A shows an indicator diagram of a piston pump according the invention part A shows the option where the piston is moving, while part B shows the option where the chamber is moving.

Fig. 102B shows an indicator diagram of a pump according to the invention where the transversal cross-section increases again from a certain point of the pump stroke, by still increasing pressure.

Fig. 103 A shows a longitudinal cross-section of a pump with fixed different areas of transversal cross-sections of the pressurizing chamber and a piston with radially-axially changing dimensions during the stroke - the piston arrangement is shown at the beginning and at the end of a pump stroke

(first embocliment).

Fig. 103B shows an enlargement of the piston arrangement of Fig. 103 A at the beginning of a stroke.

Fig. 103C shows an enlargement of the piston arrangement of Fig. 103 A at the end of a stroke.

Fig. 103D shows a longitudinal cross-section of a chamber of a floor pump according to the invention with such dimensions that the operating force remains approximately constant - as a comparison the cylinder of an existing low pressure (dotted) and high pressure floor (dashed) pump are shown simultaneously. shows a longitudinal cross-section of a pump with fixed different areas of the transversal cross-sections of the pressurizing chamber and a piston with radially/partially axially changing dimensions during the stroke - the piston arrangement is shown at the beginning and at the end of the pump stroke (second embodiment).

shows an enlargement of the piston arrangement of Fig. 104A at the beginning of a stroke.

shows an enlargement of the piston arrangement of Fig. 104A at the end of a stroke.

shows section A-A of Fig. 104B.

shows section B-B of Fig. 104C.

shows an alternative solution for the loading portion of Fig 104D.

shows a longitudinal cross-section of a pump with fixed different areas of the transversal cross-sections of the pressurizing chamber and a piston with radially-axially changing dimensions during the stroke - the piston arrangement is shown at the beginning and at the end of the pump stroke (third embodiment).

shows an enlargement of the piston arrangement of Fig. 105 A at the beginning of a stroke.

shows an enlargement of the piston arrangement of Fig. 105 A at the end of a stroke.

shows section C-C of Fig. 105 A.

shows section D-D of Fig. 105 A.

shows the pressurizing chamber of Fig. 105 A with a piston means with sealing means which is made of a composite of materials.

shows an enlargement of the piston means of Fig. 105F during a stroke.

shows an enlargement of the piston means of Fig. 105F at the end of a stroke, both while it is still under pressure and while it is not anymore under pressure. shows a longitudinal cross-section of a pump with fixed different areas of the transversal cross-sections of the pressurizing chamber and a fourth embodiment of the piston with radially-axially changing dimensions during the stroke - the piston arrangement is shown at the beginning and at the end of the pump stroke.

shows an enlargement of the piston arrangement of Fig. 106A at the beginning of a stroke.

shows an enlargement of the piston arrangement of Fig. 106A at the end of a stroke.

shows the pressurizing chamber of Fig. 106A and a fifth embodiment of the piston with radially-axially changing dimensions during the stroke - the piston arrangement is shown at the beginning and at the end of a pump stroke.

shows an enlargement of the piston arrangement of Fig. 106D at the beginning of a stroke.

shows an enlargement of the piston arrangement of Fig. 106D at the end of a stroke.

shows a longitudinal cross-section of a pump comprising a concave portion of the wall of the pressurizing chamber with fixed dimensions and a sixth embodiment of the piston with radially-axially changing dimensions during the stroke - the piston arrangement is shown at the beginning and at the end of the pump stroke.

shows section E-E of Fig. 107B.

shows section F-F of Fig. 107C. 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.

shows a variant of the pressurizing chamber of Fig.107 A, 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.

shows transversal cross-section G-G (dotted lines) and H-H of the longitudinal cross section of Fig. 107G.

shows transversal cross-section G-G (dotted lines) and I-I of the longitudinal cross section of Fig. 107H.

shows a variant of the piston of Fig. 107B, in section H-H of Fig. 107H.

shows other 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.

shows an example of an optimized convex shape of the transversal cross section under certain constraints.

shows an example of an optimized non-convex shape of the transversal cross section under certain constraints.

shows a longitudinal cross-section of a pump comprising a convex portion of the wall of the pressurizing chamber with fixed dimensions and a seventh embodiment of the piston with radially-axially changing dimensions during the stroke - the piston arrangement is shown at the beginning and at the end of a pump stroke.

shows an enlargement of the piston arrangement of Fig. 105 A at the beginning of a stroke. shows an enlargement of the piston arrangement of Fig. 105 A at the end of a stroke.

shows a longitudinal cross-section of a pump with fixed different areas of the transversal cross-sections of the pressurizing chamber and an eight embodiment of the piston with radially-axially changing dimensions during the stroke - the piston arrangement is shown at the beginning and at the end of a pump stroke.

shows an enlargement of the piston arrangement of Fig. 109A at the beginning of a stroke.

shows an enlargement of the piston arrangement of Fig. 109 A at the end of a stroke.

shows the piston of Fig. 109B with a different tuning arrangement.

shows a nineth embodiment of the piston similar to the one of Fig. 109A with fixed different areas of the transversal cross-section of the pressurizing chamber.

shows an enlargement of the piston of Fig. 11 OA at the beginning of a stroke.

shows an enlargement of the piston of Fig. 11 OA at the end of a stroke,

shows a longitudinal cross-section of a pump with fixed different areas of the transversal cross-sections of the pressurizing chamber and an tenth embodiment of the piston with radially-axially changing dimensions during the stroke - the piston arrangement is shown at the beginning and at the end of a pump stroke.

shows an enlargement of the piston of Fig. 111A at the beginning of a stroke.

shows an enlargement of the piston of Fig. 111 A at the end of a stroke,

shows a longitudinal cross-section of a pump with fixed different areas of the transversal cross-sections of the pressurizing chamber and an eleventh embodiment of the piston with radially-axially changing dimensions during the stroke - the piston arrangement is shown at the beginning and at the end of a pump stroke.

Fig. 1 12B shows an enlargement of the piston of Fig. 112A at the beginning of a stroke.

Fig. 112C shows an enlargement of the piston of Fig. 112A at the end of a stroke.

Fig. 113A shows a longitudinal cross-section of a pump with variable different areas of the transversal cross-section of the pressurizing chamber 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. 113B shows an enlargement of the arrangement of the combination at the beginning of a pump stroke.

Fig. 113C shows an enlargement of the arrangement of the combination during a pump stroke.

Fig. 113D shows an enlargement of the arrangement of the combination at the end of a pump stroke.

Fig. 114 shows a longitudinal cross-section of a pump with variable different areas of the transversal cross-section of the pressurizing chamber and a piston with variable geometrical sizes - the arrangement of the combination is shown at the beginning, during and at the end of the pump stroke.

653 BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 201 A 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. 20 IB shows the contact pressure of the pressurized piston of Fig. 201 A on the wall of the cylinder.

Fig. 202A shows a longitudinal cross-section of the piston of Fig. 201 A in a cylinder at the first (right) and second (left) longitudinal position, the piston is non- pressurized.

Fig. 202B shows the contact pressure of the piston of Fig. 202A on the wall of the cylinder at the second longitudinal position.

Fig. 202C shows a longitudinal cross-section of the piston of Fig. 201 A in a cylinder at the second longitudinal position, the piston is pressurized on the same pressure level as the one of Fig. 201 A - also is shown the piston at the first longitudinal position (production) size.

Fig. 202D shows the contact pressure of the piston of Fig. 202C on the wall of the cylinder at the second longitudinal position.

Fig. 203A shows a longitudinal cross-section of a piston of Fig. 201A 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. 203B shows the contact pressure of the piston of Fig. 203A on the wall of the cylinder.

Fig. 204A 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. 204B shows the contact pressure of the pressurized piston of Fig. 204A on the wall of the cylinder. 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. 204A.

shows the contact pressure of the piston of Fig. 204C on the wall of the cylinder.

shows a longitudinal cross-section of the piston of Fig. 204A in a non- pressurized cylinder at the second longitudinal position, the piston with its production size, and when pressurized.

shows the contact pressure of the pressurized piston of Fig. 205A on the wall of the cylinder.

shows a longitudinal cross-section of the piston of Fig. 204A in a cylinder at the second longitudinal position, the piston with its production size, and when pressurized, subjected to a pressure from the cylinder.

shows the contact pressure of the piston of Fig. 205 C on the wall of the cylinder.

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.

shows an enlargement of the piston of Fig. 206 A at the beginning of a stroke.

shows an enlargement of the piston of Fig. 206A at the end of a stroke.

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,

shows the pattern of Fig. 206D when the wall of the container has been expanded, 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,

shows the pattern of Fig. 206F when the wall of the container has been expanded,

shows production details of a piston with a textile reinforcement.

shows a longi dinal 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,

shows an enlargement of the piston of Fig. 207A at the beginning of a stroke,

shows an enlargement of the piston of Fig. 207A at the end of a stroke,

shows a longitudinal cross-section of a chamber with fixed different areas of the transversal cross-sections having different circumpherical length, and a third embodiment of the piston comprising a fiber reinforcement (no 'Trellis Effect¹) 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.

shows an enlargement of the piston of Fig. 208A at the beginning of a stroke.

shows an enlargement of the piston of Fig. 208 A at the end of a stroke.

shows a top view of the piston of Fig. 208A 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.

shows a top view of the piston alike the one of Fig. 208A 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.

shows a top view of the piston alike the one of Fig. 208A 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.

shows production details of a piston with a fiber reinforcement.

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.

shows an enlargement of the piston of Fig. 209A at the first longitudinal position of the chamber.

shows an enlargement of the piston of Fig. 209A at the second longitudinal position of the chamber.

shows the embodiment of Fig. 206 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,

shows instead of an inflation valve, a bushing enabling connection to an external pressure source.

shows details of the guidance of the rod of the check valve,

shows the flexible piston of the check valve in the piston rod.

shows the embodiment of Fig. 206, where the volume of the enclosed space of Fig. 210A-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. 21 ID.

Fig. 21 OF shows the embodiment of Fig. 10E, where there are steerable valves and a jet or a nozzle - shown as black boxes.

Fig. 211 A shows the embodiment of Fig. 206 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. 21 IB shows a piston arrangement and its bearing where the piston arrangement is communicating between the second and the first enclosed space.

Fig. 2 l lC shows a alternative piston arrangement adapting itself to the changing cross- sectional area's in its longitudinal direction inside the piston rod.

Fig. 21 ID shows an enlargement of the inflation arrangement of the piston of Fig. 211 A at the end of the stroke.

Fig. 21 IE shows an enlargement of the bypass arrangement for the valve actuator for closing and opening of the outlet valve.

Fig. 21 IF shows an enlargement of an automatic closing and opening arrangement of the outlet valve - a comparable system is shown for obtaining a predetermined pressure value in the piston (dashed).

Fig. 211G shows an enlargement of an inflation arrangement of the piston of Fig.

211 A, comprising a combination of a valve actuator and a spring-force operated cap, which makes it possible to automatically inflate the piston from the chamber to a certain predetermined pressure.

Fig. 211H shows an alternative solution for the one of Fig. 211G, comprising a combination of a valve actuator and a spring positioned below the piston of the valve actuator. Fig. 212 shows an arrangement where the pressure in the container may depend of the pressure in the chamber.

Fig. 213A 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. 213B shows an enlargement of - the arrangement of the combination at the beginning of a pump stroke.

Fig. 213C shows an enlargement of the arrangement of the combination during a pump stroke.

Fig. 213D shows an enlargement of the arrangement of the combination at the end of a pump stroke.

Fig. 214 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. 215A 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. 215B shows a variant of the pressurizing chamber of Fig. 207A, 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. 215C shows transversal cross-section G-G (dotted lines) and H-H of the longitudinal cross section of Fig. 215B.

Fig. 215D shows transversal cross-section G-G (dotted lines) and I-I of the longitudinal cross section of Fig. 215C.

shows other 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.

shows an example of an optimized convex shape of the transversal cross section under certain constraints. ·

shows a combination where the piston in moving in a cylinder over a tapered center.

shows an ergonomical optimized chamber for pumping purposes and manual operation.

shows the corresponding force-stroke diagram.

shows an example of a Movable Power Unit, hanging under a parachute,

shows details of the Movable Power Unit.

507 DESCRIPTION OF THE DRAWINGS

The foregoing features and other aspects of the invention are explained in the following

description in connection with the accompagning drawings, wherein: Figure 301 shows a first embodiment of the valve actuator in a clip-on valve connector to which a Schrader valve can be coupled,

Figure 301 A shows an enlargement of a detail of Figure 301 with channels around the piston,

Figure 301B shows section G-G of Figure 301A,

Figure 302 shows a second embodiment of the valve actuator in a universal clip-on valve connector with a streamlined activating pin,

Figure 302A shows an enlargement of a detail of Figure 302,

Figure 302B shows section H-H of Fig. 302A,

Figure 303 shows a third embodiment of the valve actuator in a squeeze-on valve connector,

Figure 303A shows an enlargement of a detail of Figure 303,

Figure 304 shows the valve actuator including an activating pin and the wall of the cylinder in a permanent assembly (e.g. from a chemical plant),

Figure 305 shows a fourth embodiment of the valve actuator in a universal valve connector.

19597 BRIEF DESCRIPTION OF THE DRAWINGS

In the following, preferred embodiments of the invention will be described with reference to the drawings wherein the invention is explained in detail below by means of diagrams and drawings. The following is shown in the diagrams or drawings - a transversal cross-section means a cross-section perpendicular to the moving direction of the piston and/or the chamber, while the longitudinal cross-section is the one in the direction of said moving direction:

Fig. 401 A shows a top view of a pump of a floor pump type of Fig 40 IB, where the combination can turn around a line XX, YY or ZZ in relation to the floor surface, while the angle is not restricted by the suspension.

Fig. 401 B shows a back view of the floor pump of Fig. 401 A.

Fig. 402A shows top view of a pump of a floor pump type of Fig 402B, where the combination can move in 3 dimensions in relation to the surface, while the angle is restricted by spring force of the. transition between the combination and the basis.

Fig. 402B shows the back view of the floor pump.

Fig. 402C shows a top view of the pump of Fig 402B, where the handle has been moved to a position in front of its rest position.

Fig. 402D shows a top view of the pump of Fig 402B, where the handle has been moved to a position at the back of its rest position.

Fig. 402E shows a top view of the pump of Fig 402B, where the handle has been moved to a left position in front of its rest position.

Fig. 402F shows a top view of the pump of Fig 402B, where the handle has been moved to a left position at the back of its rest position.

Fig. 402G shows a top view of the pump of Fig 2B, where the handle has been moved to a right position in front of its position when out of function.

Fig. 402H shows a top view of the pump of Fig 402B, where the handle has been moved to a right position at the back of its rest position.

Fig. 403A shows a side view of a floor pump with a flexible transition between the

chamber of the combination and the basis. Fig.403B shows an enlargement of the transition of Fig. 403 A.

Fig. 403C shows a back view of a floor pump with another flexible transition between the chamber of the combination and the basis.

Fig. 403D shows an enlargement of the transition of Fig. 403C.

Fig.404A shows a back view of a floor pump with a cab which allows the piston rod to move in the transversal direction of the combination.

Fig. 404B shows an enlargement of a transversal - cross-section of the cab of

Fig. 404A when the piston rod is pulled out to its maximum - no transversal movement.

Fig. 404C shows the transversal cross-section of Fig. 404B when the piston rod is pulled out to its maximum, with a rotation o the piston rod to the left.

Fig. 404D shows an enlargement of a transversal cross-section of the cab of

Fig. 404A when the piston rod is not pulled out - no transversal movement.

Fig. 404E shows the transversal cross-section of Fig. 404D when the piston rod is not pulled out, with a transversal translation of the piston rod to the left.

Fig. 405A shows a top view of a floor pump type of Fig 405B, where the angle between the centerlines of the handle parts opposite the centerline of the combination is less than 180°.

Fig. 405B shows a side view of handle of the floor pump of Fig. 405 A.

Fig. 406A shows a top view of a floor pump type of Fig 406B, where the angle between the centerlines of the handle parts opposite the centerline of the chamber is more than 180°.

Fig. 406B shows a side view of handle of the floor pump of Fig. 406 A.

19627 DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 1-3 deal with the limitation of the stretching of the wall of the piston. This comprises a limitation of the stretching in the longitudinal direction when the piston is 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.

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.

The expansion behaviour of the wall of the container may be depending on the type of the stretching limitation used. Moreover, 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 subjected to external forces.

All kinds of fluids may be used - a combination of a compressable and a non-compressible medium, a compressable medium only or a non-compressable medium only.

As 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. In order to keep the pressure in the chamber, 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. 1A shows a longitudinal cross-section of the chamber 186 with a concave wall 185 and an inflatable piston comprising a container 208 at the beginning (= first longitudinal position in the chamber 186) and the same 208' at the end of a stroke (= second longitudinal position in the chamber 186). Central axis of the chamber 186 is 184. The container 208' shows its production size, having a textile reinforced 189 in the skin 188 of the wall 187. During the stroke, 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. Depending on the pressure in the chamber 186, there still may occur a longitudinal stretching of the wall of the container, due to pressure in the chamber 186. The main function however of the reinforcement is to limit this longitudinal stretching of the wall 187 of the container 208. During the stroke 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 circumferential 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. IB shows a first embodiment of the expanded piston 208 at the beginning of a stroke. The wall 187 of the container is build up by a skin 188 of a flexible material, which may be e.g. a rubber type or the like, with a textile reinforcement 189, which allows expansion. The direction of the textile reinforcement in relation to the central axis 184 (= braid angle) is different from 54°44'. 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 end of the stroke (= second longitudinal position). An impervious layer 190 inside the wall 187 may be present. It is tightly squeezed in the cap 191 in the top and the cap 192 in the bottom of the container 208, 208'. 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 can 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 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 the wall 185a of the chamber 186 which is parallel to the centre axis 184. It is positioned approx. at the end of the stroke at first longitudinal positions. (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. The contact area between the wall of the container and the wall of the chamber is 198.

Fig. 1C shows the piston of Fig. IB at the end of a pump stroke, where it has its production size. 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 is pressure in the chamber 186, then the bottom cap 192 is pressed against the stop 197. The compressable fluid 206' and the non-compressable fluid 205'. The contact area 198' between the container 208'and the wall of the chamber at the second longitudinal position.

The wall 185b of the chamber 186, which is parallel to the centre axis 184. It is positioned approximately at the end of the stroke at second longitudinal positions

Fig.2A 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 its production size, having a fiber reinforcement 219 in the skin 216 of the wall 218 according to the Trellis Effect . During the stroke the wall 218 of the container expands until a stop arrangement, which may be the fiber reinforcement 219 and/or a mechanical stop 214 inside the container and/or another stop arrangement stops the movement during the stroke. And thus stops the expansion of the wall 218 of the container 217. The main function of the fiber reinforcement is to limit the longitudinal stretching of the wall 218 of the container 217. During the stroke the pressure inside the container 217, 217' may remain constant. This pressure depends on the change in the volume of the container 217, 217', thus on the change in the circumferential length of the cross-sections of the chamber 186 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. The contact area 211 between the container 217 and the wall of the chamber at the first longitudinal position.

Fig. 2B shows a second embodiment of the expanded piston 217 at the beginning of a stroke. The wall 218 of the container is build up by a skin 216 of a flexible material, which may be e.g. a rubber type or the like, with a fiber reinforcement 219, which allows expansion of the container wall 218, and thus the direction of the fibers in relation to the central axis 184 (= braid angle) may be different from 54°44'. Due to the expansion the thickness of the wall of the container may be smaller, but not necessarily very different than that of the container as produced when positioned at the end of the stroke (= second longitudinal position). An impervious layer 190 inside the wall 187 may be present. It is 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 can 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 can 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. 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 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. 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.

The wall 185a of the chamber 186, which is parallel to the centre axis 184. It is positioned approximately at the end of the stroke at first longitudinal positions Fig. 2C shows the piston of Fig. 2B at the end of a pump stroke, where it has its production size. The cap 191 is moved over a distance c' from the stop 214. 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 cap 192 is pressed against the stop 197. The compressable fluid 206' and the non-compressable fluid 205'. The contact area 21 Γ of the container 217'and the wall of the chamber 186 at the second longitudinal position.

The wall 185b of the chamber 186, which is parallel to the centre axis 184. It is positioned approximately at the end of the stroke at second longitudinal positions.

Fig. 3A,B,C show an inflatable piston comprising a container 228 at the beginning and 228' at the end of a stroke. The production size is that of piston 228'at the second longitudinal position in the chamber 186. The construction of the piston may be identical with that of Fig. 7AJ3,C with the exception that 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. 3B shows the wall 218 with the skin 222 and 224. The reinforcement 223. The contact area 225 between the container 228 and the wall of the chamber at the first longitudinal position. The impervious layer 226.

Fig. 3C shows the contact area 225 ' between the container 228' and the wall of the chamber at the second longitudinal position.

Fig. 3D shows a top view of the piston 228 and 228', respectively with the reinforcement means 227, and 227' respectively.

Fig. 3E shows a top view of the piston 228 and 228', respectively with the reinforcement means 229, and 229' respectively.

Fig. 4 shows a non-moving expandable piston 228' inside a chamber 186 with a wall 185a, which is parallel to the centre axis 184 of said chamber 186 at a position where the contact surface 225' between the piston 228 "and the wall 185 of said chamber 186, while there are no pressure differences in the chamber between both sides of said piston. The part 185 of the chamber further to a first position has an angle a with the centre axis 184. The projection 1000 of the middle point (centre) 1001 of the elastically deformable wall of the piston on the centre axis 184.

Fig. 5 A shows the piston of Fig. 4, instantaneously non-moving inside a chamber 186 with a conical shaped wall 185, where the piston is beginning to expand - the movable cab 191 is moving toward the non-movable cab 192. The contact surface 225" has been increasing, and is now positioned below the centres 1002 and 1003, respectively of the elastically deformable wall of the piston - its projection on the centre axis 1004 (old) and 1005 (new), respectively. The distance f . The direction of moving 1006 of the movable cab 191. The force 1007 from the wall 187 of the piston to the wall 185 of the chamber 186. The distance g'.

Fig. 5B shows the piston of Fig. 5 A, instanteneously non-moving, and thereby expanding, so that the contact area 225"' of the piston wall 187 with the 185 wall of the chamber 186 increases at second longitudinal positions of said contact surface 225"' - the movable cab 191 is currently non- moving. The contact surface 225'" is around the point where the middle point (centre) is of the elastically deformable wall of the container. The centres 1008 (old) and 1009 (new) of the elastically deformable wall of the piston - its projections 1010 (old) and 1011 (new) on the centre axis 184 respectively. The distance f . The force 1012 from the piston wall 187 on the wall 185 of the chamber. The direction of movement 1013 of the force 1012. The movement 1014 of the movable cap 191.

Fig. 5C shows the piston of Fig. 5B, instanteneously non-moving, and thereby expanding, so that the contact surface 225"" of the piston wall 187 with the wall 185 of the chamber decreases at second longitudinal positions of said contact area, while the contact area of the piston wall with the wall of the chamber increases at first longitudinal positions of said contact area - the movable cab is non-moving. The centres 1015 (old) and 1016 (new) of the elastically deformable wall of the piston - its projections 1017 (old) and 1018 (new) on the centre axis 184 respectively. The distance g'. The direction of movement 1019 of the reaction force 1020 of the chamber wall 185 on the wall 187 of the piston. The direction of the movement 1021 of wall 187 of the piston.

Fig. 5D shows the piston of Fig. 5C, where the non-movable cap 192 is instanteneously beginning to move from second to first longitudinal positions, thereby moving the piston in the same direction. The contact area 225'"", which is much smaller than that 225"" of Fig. 5C. The distance h'. The projection 1022 of the centre 1023 of the elastically deformable wall of the piston on the centre axis 184 respectively. The moving direction 1024 of the movable cap 191, and that 1025 of the non-movable cab 192, thus that of the whole piston. The leakage 1026, which occurs at that point of time.

Fig. 5E shows the piston of Fig. 5D, where the movement of the piston is decreasing due to a increasing contact area 225 The projection 1027 on the centre axis 184 of the centre 1028 of the elastically deformable wall of the piston. The moving direction 1029 of the movable cap 191. The moving direction 1030 and 1031 of the wall of the piston.

Fig. 6 A shows an expandable piston 898, moving engagingly or/and sealingly 900 in a cone-formed chamber 899,comprising a reinforced (not shown) wall 901, which is embedded in immovable cab 903, and a movable cab 904. Said cab 904 is slidingly movable over the piston rod 902, which is hollow, comprising the enclosed space, and communicating with the space in the piston 898. There is fluid or a mixture of fluids in the piston. Said chamber is closed at both sides of the piston with spaces 906, 907, and may be comprise a fluid or a mixture of fluids at one or at both sides of the piston 898. The contact area 905 between the wall 901 of the piston 898 and the wall 897 of the chamber 899. The existence of fluid at both sides of the piston may cause the piston move in a different manner than desired.

Fig. 6B shows the piston 898 of Fig. 6A moving engagingly or/and sealingly 900 in a cone-formed chamber 896,which has spaces 908 and 909 at the respective sides of the piston 898. In the wall 895 of the cone formed chamber 896 at 1^st longitudinal positions is a tube 911, which allows communication between the space 908 with the atmosphere 910 of the surroundings,while tube 912 is assembled in the wall 895 of said cone-formed chamber 896, which allows communication between the space 909 with the atmosphere 910 of the surroundings. The contact area 905 between the wall 901 of the piston 898 and the wall 897 of the chamber 896. the atmosphere 910 of the surroundings. The contact area 905 between the wall 901 of the piston 898 and the wall 897 of the chamber 896

Fig. 6C shows the piston 898 of Fig. 6A moving engagingly or/and sealingly 900 in a cone-formed chamber 894, which has spaces 908 and 909 at the respective sides of the piston 898. In the wall 893 of the cone formed chamber 894 at 1^st longitudinal positions is a tube 913, which allows communication between the space 908 with the inside of tube 915 which communicates with the tube 914, which is assembled in the wall 893 of said cone-formed chamber 896, and which communicates with the space 909 of said cone-shaped chamber 894. The contact area 905 between the wall 901 of the piston 898 and the wall 893 of the chamber 896.

Fig. 6D shows the piston 892 moving engagingly in a cone-shaped chamber 899, which has spaces 906 and 907 at the respective sides of the piston 892. Said spaces 906 and 907 are communicating with each other through tube 918, which is assembled in cabs 891 and 890, respectively. The contact area 905 between the wall 901 of the piston 898 and the wall 897 of the chamber 899.

Fig. 6E shows the piston 898 engagingly movable in a cone-shaped chamber 899 Said chamber is closed at both sides of the piston with spaces 906, 907, and may be comprise a fluid or a mixture of fluids at one or at both sides of the piston 898. There is no contact area between the internal wall 922 of the cone-formed chamber 899 and the external wall 923 of the piston 924, and instead there is a gab 920 between said walls 922 and 923, allowing a flow of fluid 921 in the opposite direction of the motion 900 of said piston 898.

Fig. 6F shows an actuator piston 925, based on the piston 924 shown in Fig. 6E, having a duct

926, preferably 3 ducts 926 equally spread over the contact area 927 of the wall 928 of the actuator piston 925 and the wall 922 of the chamber 899. The ducts 926 are allowing communication of the fluid between both spaces 906 and 907 of the chamber 899. The part 929 of the contact area 927 where sealingly contact is taking place with the wall 922 of the chamber 899 along the circumference is smaller, than when said ducts 926 were not present, but the obtained driving force of said actuator piston 925. may still be acceptable. The length of said duct 926 in the longitudinal direction is bigger than longitudinal length of the contact area 927 in order to obtain communication between said spaces 906 and 907 of said chamber 899, at all longitudinal positions. The piston rod 929. The movable cab 930.

Fig. 6G shows the a transversal cross-section of the piston rod 929 of Fig. 6F and the view on the actuator piston 925 from a 1^st longitudinal position. The chamber wall 922. The movable cab 930. The ducts 926, equally updividing the circumference of said actuator piston 925 approx. at the contact area 927 with the wall 922 of said chamber 899.

Fig. 7A shows the piston of Fig. 1C at the end of a pump stroke. The wall of the chamber is parallel with the centre axis 184, and which is why the container is non-moving, even when pressurized.

Fig. 7B shows the piston of Fig. 7A, in a part of the chamber where the walls are not paralell to the centre axis, but with a positive angle. The piston will move toward a first position, because the mid point of its flexible wall is above the contact surface with the wall.

Fig. 7D 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 53°44'. When the material type and thickness is the same for all layers, and the number of layers even, while the stitch sizes for each direction are equal, the expansion and contraction of the wall of the container may be equal in the XYZ-direction. When expanding the stitch ss and tt, respectively in each of the directions of the matrix will become bigger, while contracting these wil become smaller. As 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. 7B.

Fig. 7E is a 3-dimensional drawing and shows the reinforcement matrix of Fig. 7D 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. 7D.

Fig. 7F 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. When the wall of the container is expanding the inelastic material (but elastically bendable) may limit the maximum expansion of the wall 187 of the container 217. It may be necessary to stop the movement of the container 217 over the piston rod 195 by e.g. stop 196, so that sealing may remain. The lack of such a stop 196 may give the possibility of creating a valve.

Fig. 7G is a 3-dimensional drawing and shows the reinforcement matrix of Fig. 7F 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. 7F. Fig. 8 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 here 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).

All solutions disclosed in this document may also be combined with piston types for which the chambers having cross-sections with constant circumpherential sizes may be the solution for the problem of jamming.

Fig. 9A shows a longitudinal cross-section of the chamber with a convex/concave wall 185 and an inflatable piston comprising a container 258 at the beginning and the same 238' at the end of a stroke. The container 258' shows its production size.

Fig. 9B shows the longitudinal cross-section of the piston 258 having a wall 251 and a reinforced skin 252 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'. The contact area 253.

Fig. 9C shows the longitudinal cross-section of the piston 258'. The contact area 253'. Fig. 9D shows the longitudinal cross-section of the piston 258" with a common area 253". The centre 1020 of the elastically, deformed wall 251 of the piston. The projection of the centre point 1020 on the centre axis 1022.

Figs. 10A-F (incl.) show the pressure arrangement of a combination of an inflatable actuator piston, running in a chamber, said chamber having cross-sections of different cross- sectional areas and different circumferential lengths at the first and second longitudinal positions, and at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross- sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longitudmal position, wherein the size of the volume of the enclosed space is constant when the said actuator piston is running from a second to a first longitudinal position. This may be done in both technologies (CT and ESVT).

Figs. 10G-L (incl.) show the pressure arrangement of a combination of an inflatable actuator piston, running in a chamber, said chamber having cross-sections of different cross-sectional areas and different circumferential lengths at the first and second longitudinal positions, and at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longitudinal position, where the size of the enclosed space is decreasing when said actuator piston is running from a second to a first longitudinal position. This is done in order to reduce the volume of the pressurized medium, and thus is a reduction of the energy to be used for the repressuration of said medium. This may be preferably done in embodiments using the ESV Technology, because there the change of the size of the enclosed space volume is done much more easily than in embodiments using the Consumption Technology.

Fig. 10A shows a piston-chamber combination with a chamber 186, having a centre line 184, a wall 185 of said chamber 186, where a pressurized ellipsoi^'de shaped piston 217' - as described in sections 207, 653, 19660 and 19680 of this patent application - is moving 2003 from a second longitudinal position 2000 to a first longitudinal position 2001. At said first longitudinal position 2001 has said piston 217' been expanding into a piston 217, having a sphere shape, while having a fixed volume of the enclosed space 210. This means that the pressure inside said piston 217 gradually during the movement 2003, and is at its lowest value at the first longitudinal position 2001. The shape of the piston 217 may also be at said first longitudmal position be ellipsoide (not shown) - as described and shown in section 19660 of this patent application - and this will result in a less increase in pressure of said piston. The position 2004 of the valve 126 is during said run unchanged, so that the volume of the enclosed space 210 remains unchanged. The arrow 2005 shows that the next stage of the operation is shown in Fig. 10B or Fig IOC, the last mentioned shown by the arrow 201 1.

The position 2025 shows the piston 217' at a second longitudinal position, where the wall

2030 of said chamber 186 is parallel to the centre axis 184. The position 2026 of piston 217 at a first longitudinal position, where the wall 2031 of of said chamber 186 is parallel to the centre axis 184. The shape 2027 shows said piston 217, when at a first longitudinal position, the piston is (delayed) beginning to depressurizing. Shape and size 2028 is when the piston 217" is approximately on half of the return stroke, where it is just free of the wall 185 of the chamber 186, due to a delayed depressuration. The same shape and size 2028 of the piston 217' may be positioned closer (distance y) to a second longitudinal position than when the piston 217" is moving to a second longitudinal position, as said piston 217' is engaging the wall 185 of said chamber 186 (and not free of it).

The size of the enclosed space under the valve 126 is determined by the length of the channel to the bottom of the piston rod - this length is 'a' at a 2^nd longitudinal position and is 'b' at a 1^st longitudinal position, wherein a = b.

Fig. 10B shows the valve 126 has been retracted 2006 from the its position 2004 to a position 2007 further away from said piston 217. The enclosed space 210'. The result is that the volume of the enclosed space 210' is decreasing so much that the pressure inside the piston 217" has

become approximately that of when said piston had been produced (e.g. atmospheric pressure) - the size and shape are approximately those of when the piston is on the second longitudinal postion 2000, but now unpressurized - this means that the piston 217" may not engaging and/or may engaging, but not seal the wall 185 of said chamber 186, when returning 2008 from the first longitudinal position 2001 to the second longitudinal position 2000. The wall 2024 of the piston.

When the piston 217" is moving 2008 from a first 2001 to a second 2000 longitudinal position, may the internal pressure drop be so relatively slowly obtained, that the piston 217B"during said moving still may have an ellipso^'ide shape larger than that of the shape of 217' at a second longitudinal position 2000, so that said piston 217B" during said moving 2008 is engaging and/or non-engaging the wall 185. As a comparison: the same size of said piston 217B" is obtained further away to a 2^nd longitudinal position than when the piston is (sealingly and/or engagingly) moving 2003 from a 2^nd longitudinal position 2000 to a 1^st longitudinal position 2001. Said pressure drop may also be obtained already at a first longitudinal position 2001.

When the piston 217", 217B" has returned to the second longitudinal position 2000, the position of valve 126 in the enclosed space 210' changes from 2007 to 2004 - arrowed 2009, so that the enclosed space 210' has got its original volume of Fig. 10A again, so that said piston 217' again has its original pressure. The arrow 2010 shows that the next stage of the operation shown in Fig. 10A.

Fig. IOC shows the alternative solution for changing the internal pressure of the piston 217, and shall be regarded together with Fig. 10A, where in this case the valve 126 is lacking and instead may an inlet/outlet configuration 2020 be present - e.g. please see Figs. 210A-F (incl.) and Figs. 211A-F (incl.) of section 653 of this patent application. The pressurized piston 217' is moving 2003 from the second longitudinal position 2000 to the first longitudinal position 2001, as described in Fig. 10A. No adding or removing fluid from the enclosed space 210 is occuring. The arrow 2011 shows that the next stage of the operation is shown in Fig. IOC. The depressurization in piston 217" is obtained by removing the necessary amount of fluid from the enclosed space 210: arrow 2020. When said piston 217" has been returned from the first longitudinal position 2001 to (arrow 2021) to the second longitudinal position 2000, sufficient fluid is added (arrow 2022) to the enclosed space 210, resulting in piston 217'" - the arrow 2023 shows that the next phase is shown in Fig. 10A, resulting in piston 217'. The wall 2024 of the piston.

It should be emphasized that a combination of both above mentioned technologies may be an additional solution for the pressure management of the piston. It may additionally be possible that the

pressure drop from piston 217 or 208 to piston 217" or 208", respectively may be a gradual one - e.g. computerized - on the condition that the wall 2024 of the piston only is engaging the wall 185 of the chamber 186 or not at all during the return from a 1^st longitudinal position 2001 to a 2^nd longitudinal position 2000.

The wall 185 of the chamber 186 in the drawings 10A-L at the second and first longitudinal positions may be not parallel to the centre axis. No channels as shown in Figs. 4, 5A-E (incl.),

Figs. 10D-F show the analogue process of that shown in Figs. lOA-C, now with a sphere shaped piston 208.

Figs. 10G-I show an analogue process of that shown in Figs. lOA-C, with the difference that the pressure may be maintained more when the piston 217^? is moving from a 2^nd longitudinal positions 2000 to a first longitudinal position 2001, wherein the valve 126 is not so much removing from the bottom end of the piston, as shown in Fig. 1 OA. The length of the piston rod under piston 126, which is giving the size of the enclosed space volume, is 'e', while between 2^nd and 1^st longitudinal positions this length has been decreased to 'f and at a 1^st longitudinal position said length is further decreased to 'g', wherein e > f > g.

Figs. 10J-L show the comparable process of that shown in Figs. 10D-F, wherein pressure is maintained as described in Fig. 10G, but now with a sphere shaped piston 208. The length of the piston rod under valve 126, which is giving the size of the enclosed space volume, is 'h', while between 2^nd and 1^st longitudinal positions this length has been decreased to 'i' and at a 1^st longitudinal position said length is further decreased to 'j', wherein h > i > j. The process called the E(nclosed)S(pace)V(olumechange) T(echnology) shown in Figs. 10A,10B or Figs. 10D,10E are being used in a motor according this invention, shown in Figs. 11F,G (crankshaft) and in Figs, 13F, 13G, 14A-H (incl.) (rotational).

The process called C(onsumption) T(echnology) shown in Figs. 1 OA, IOC or Figs. 10D,10F and in Figs. 210A-F (incl.) and Figs.211A-F (incl.) are being used in a motor according this invention, shown in Figs. 11 A-C (incl.) (crankshaft) and in Figs. 12A-C (incl.), 13A-D (incl.).

Fig. 10M shows B-B section of Fig. 12 C (and said B-B section can be partly seen on Fig. 12A) and the motor where the piston of an actuator piston-chamber combination is moving, while the chamber is not moving. The motor comprising a chamber 960, which is comprising 4 sub-chambers 961, 962, 963 and 964, respectively, which lie around the same centre axis 965 in continuation of each other, which has an axle 966 through the center 967 of said chamber 960. Within said sub-chambers 961, 962, 963 and 964, respectively is 1 piston 968 positioned, shown on two important positions, namely position 968' when at a 1^st rotational position of the sub-chamber 964, having the largest diameter, and position 968" when at a 2^nd rotational position of the sub-chamber 961, which is lying in continuation with sub-chamber 964, so that the 1^st rotational position of sub-chamber 964 lies closest to the 2^nd rotational position of sub-chamber 961, where it has its smallest diameter. Said actuator piston 968 is rotating clockwise around said axle 966 - there are shown 4 holes 970 for assembling said chamber 960 on axle 966.

Fig. 10N shows the B-B section of Figs. 13A and 13B and the motor is of a type where the chamber of an actuator piston-chamber combination is moving, and the piston is not moving.

The motor comprising a chamber 860, which is comprising 4 sub-chambers 861, 862, 863 and 864, respectively, which lie around the same centre axis 865 in continuation of each other, which has an axle 866 through the center 867 of said chamber 860. Within said sub-chambers 861, 862, 863 and 864, respectively are 5 pistons 868, 869, 870, 871 and 872, respectively positioned, each at a different rotational position said sub-chambers 861, 862, 863 and 864, on an angle a = 72° from each other. Each piston comprising a piston rod 873, 874, 875, 876 and 877, respectively. The pistons 868, 869, 870, 871 and 872 are of a "sphere - sphere" type, and are shown all having different diameters. Said chamber 860 is rotating clockwise around said axle 866 and the sub-chambers 861, 862, 863 and 864 having a second rotational position and a first rotational position in the clockwise rotational direction - there are shown 4 holes 878 for assembling said chamber 860 on axle 866. The motor according to Figs. 10G and 10H may comprise a chamber 860 of which, at least a part, may be parallel to the centre axis of said chamber (not shown).

The circular chamber, comprising identical sub-chambers may comprise an actuator piston in each of the sub-chambers, wherein all actuator pistons are located at the same circular point of each sub- chamber

19615 amended - Regarding a pressure management system for Figs. 1 IF, 13F and Fig. 13E

It depends on the system of the bidirectional actuator (e.g. Fig. 1 IF references 1056 and 1057) whether or not a repressuration system is necessary, when the change of direction may cause a loss of pressure - this may be caused by a "consumption" of fluid, where the fluid during the directional change may be realesed to the atmosphere or it may also be caused by a pressure drop - please see Fig. 13E. The repressuration system is than alike those shown in earlier drawings, e.g. Figs. 11 A, 1 IB and Fig. 12A.

It may possible to develop a system which does not "consume" fluid, and possibly only "consume" pressure. In the drawings Fig. 1 IF, 13F it is assumed to be present already, so that only a pressure storage vessel of a certain volume may be necessary. The pressure should be preferably low pressure (e.g. 10-15 Bar), optionally high pressue (e.g. 300 Bar).

This system may comprising a classic cylinder, in which a bidirectional piston is positioned. On each sides of the piston has the cylinder an inlet and outlet valve, so that the inlet valve of one side is communicating with an outlet valve at the other side of the piston. Thus the total accumulated volume on both sides of said piston may remaim constant - this may lead to the fact that it is possible to move the piston from one side of said cylinder to another side, without consuming fluid. Either pressure is consumed. That means that there only would be e.g. electricity present for controling said valves, and this could very well come from an accumulator which is loaded by a sustainable power source, e.g. a solar photovoltaics cell e.g. a volt and/or a generator which may be connected to a main axle. This reduces the energy needed still more for this motor. We assume, that the pressure storage vessel has been loaded at the production of the motor. Instead of the bidirectional actuator an electric step motor may be used, controlled by a computer. Such a motor may be precisely and quickly enough react on controling impulses from said computer.

Or, the system shown in Fig. 13F references 1093 and 1094 may be used here. Addition to the description of preferred embodiments for Fig. 1 IF The holes in the piston rod 805 within the container piston 810 have not been shown in the container piston 810 - these however have been shown already in Figs. 2B, 2C, reference 201 , and should be present in the Fig. 1 IF.

Addition to the description of preferred embodiments for Fig. 13F

The holes in the piston rod 805 within the container piston 810 have not been shown in the container piston 810 - these however have been shown already in Figs. IB, 1C, reference 201 , and should be present in the Fig. 13F.

Regarding the pressure management system for Figs. 11A, 1 IB, 11C

When an actuator piston, which is connected to the main axle by a crankshaft, where the fluid within said actuator piston is depressurized, and thereafter pressurized by a system, where the space within the piston is sequentially connected and disconnected with a repressuration pump and a pressure storage vessel, respectively, (Figs. 11 A, 11B, 11D), the following remarks are being made.

Just when having reached the turning point at the farthest second longitudinal position, when an actuator piston - depressurized - is moving from a first to a said second longitudinal position, a communication is made between the pressure vessel (e.g. Fig. 1 IB - ref. 314) and actuator piston, so that the piston is being pressurized immediately when having been at the farthest second longitudinal position. At that moment, there is (shortly) an open connection through two holes, one in the crankshaft and one in the connection rod, between said pressure storage vessel through the second enclosed space of said crankshaft and the enclosed space of the piston rod, and the holes in said piston rod within the container, which continuously communicate between the space within said container and the enclosed space.

This means that during the stroke from a second to a first longitudinal position the enclosed space of said piston has temporary a constant volume, which means that due to the increasing volume of said container (from ellipso^'ide with a smaller circumference to an ellipso^'ide with a bigger circumference / ellipsoide - sphere / sphere with a small diameter to a sphere with a bigger diameter), when moving, that the internal pressure within said container is being reduced continuously.

And when arriving to the farthest first longitudinal position, the internal pressure of said container may have been reduced, but may not have become to atmospheric level. Just before or just at the returning point at the farthest first longitudinal position, when returning to a second longitudinal position, a communication may take place between the space within the container, the holes between said space and the enclosed space of said container within the piston rod and the connection rod, with the third enclosed space in the crankshaft through two holes, which at that point of time have corresponding centre axles, one in said connection rod, the other in the crankshaft. The pump, which communicates with said third enclosed space and is, at that moment, sucking for fluid from said container, so that the container is depressurized.

The second enclosed space may be pressurized constantly by a constant open communication with the pressure storage vessel. It may also that this connection is controlled by a valve.

Addition to the description of preferred embodiments for Fig. 1 1 A, 1 IB, 11C.

The holes in the piston rod 805 within the container piston 810 have not been shown in the container piston 810 - these however have been shown already in Fig. 2B and 2C, reference 201, and should be present in the Figs. 11A, 1 IB and 11C

Regarding a pressure management system for Figs. 12A, 12B, 12C, 13 A, 13B

In the case of a circular chamber, which is a chamber having a central axis which is circleround, with the same pressurization system as earlier mentioned for a crankshaft solutions (Figs. 11 A, 1 IB, 11D), similar solutions may be valid in said circular chambers, but in a bit adapted way.

In case of a moving piston and a non-moving chamber (Figs. 12 A, 12B, 12C) the sphere piston may be comprising an enclosed space which may be communicating trough a hole in the piston rod, with the space inside the container, and at the other end may the enclosed space communicating with a second enclosed space, which may be positioned in the main axle. The last mentioned may be communicating with a two way valve in a housing, which may be build around the main axle. A separator valve may be a T-valve, of which the shared portion is communicating with said second enclosed space. One of the non-shared portions may be communicating with a pressure storage vessel (e.g. reference 814) (high pressure) and the other (lower pressure) with the pump (e.g. reference 818). The control of which way said separator valve is opening and closing may be done by a computer, which is monitoring the position of the main acle in comparison with the opening of the enclosed space and the opening of the second enclosed space in said main axle. It may also be done by a camshaft, which is communicating with the main axle. Because the number of single chambers is 4 in Figs. 12A and 12B, there ought to be 4 outlet/inlets to the second enclosed spaces be in the main axle, and also 4 inlets/outlets to the T- valve, or there may exist 4x T-valves. Between the T-valve (low pressure end) and the pressure storage vessel (e.g. reference 814) a pump (e.g. references 818, 826) may be added, so that the pressure is lifted up to a bit over the pressure in said pressure storage vessel. All this makes this solution be non-optimized, e.g. the transitions from and to the second enclosed space in the main axle may cause leakages.

In case a piston is non-moving and a chamber is moving (Figs. 13 A, 13B), there may be e.g. 5 pistons, each in a subchamber, which all have the same central circleround axis, while all subchamber are positioned in continuation of each other, and are communcating with each other. Each piston is communicating with a T-valve in the same way as mentioned above in case the piston was moving and the chamber non-moving. Also the pressurization system may be alike - the only difference is that there are 5 T-valves, which may be opening/closing at different point of times, as the position of each piston may be different in identical subchambers.

Instead of piston pumps may centrifugal pumps be used (Fig. B). The efficiency of centrifugal pumps may be lower than that of the piston pumps with a conaical shaped chamber..

Addition to the description of preferred embodiments for Figs. 12A-C, 13A-F

The holes in the piston rod 805 within the container piston 810 have not been shown in the container piston 810 - these however have been shown already in Figs. IB, 1C, reference 201, and should be present in the Figs. 12A-C, 13A-F.

Addition to the description of preferred embodiments for Fig. 12C.

The return channel 1 150 from the 1074 to the pump 1151, of which exit is connected by channel 1152 to the storage pressure vessel 1075. The pump 1151 may be connected (not shown) to the main axle 966 and/or to an external sustainable energy source, such as solar power (not shown).

Addition to the description of preferred embodiments for Figs. 12A-C (incl.), 13A-F (incl.).

Addition to the description of preferred embodiments for Figs. 13A,13B, 13E.

The valve box 1160 is comprising 5x T-valves 1161 - 1165 (incl.) which are opening up for either the communication [829] from the pressure storage vessel 814 to each of the pistons 868, 869, 870, 871, 872 (see Fig. 13C) through piston rods 873, 874, 875, 876, 877, or to channel [817] to a repressuration pump 818, and indirectly to 826.The pressurized return channel [825] and/or [828] from said pumps to the pressure storage vessel 889. The return channel 1 150 from the 1074 to the pump 1151, of which exit is connected by channel 1152 to the storage pressure vessel 1075. The pump 1151 may be connected (not shown) to the main axle 966 and/or to an external sustainable energy source, such as solar power (not shown).

19627 - based on 19618 - updated Figs 11A-Z based on 19617 (in main document 19601)

Fig. 1 1 A shows schematically the overall system for a ('green') motor, which is complying to all demands, as stated in the Background of this invention chapter. On a schematically drawn crankshaft 800 with a U-shaped axle 801, with axle bearings 802 and 803, contraweights 804, is a piston rod 805 assembled, which is on the other side of said piston rod 805, connected to an expandable piston 806, which is shown Left "L" in a movement (arrowed) from first to second longitudinal positions, and Right "R" in a movement (arrowed) from second to first longitudinal positions. Said piston 806 is engagingly movable in a chamber 807 with an internal wall 808. Said chamber 807 has cross-sections with continuously differing cross-sectional area's and differing circumferences, and of which the internal wall 808 has a circumference which is at second longitudinal positions smaller than at first longitudinal positions. The piston 806 has been produced, so that its unstressed production size of the circumference is approximately the size of the circumference of the wall 808 of said chamber 807 at a second longitudinal position. Said piston 806 is connected to the piston rod 805 by a cap 809, while the flexible wall 810 of said piston 806, is comprising reinforcement means 81 1, and is connected to the piston rod 805 by a slidable cap 812, which can slide over the piston rod 805. When said piston 806 being positioned at a second longitudinal position, and is communicating through its enclosed space 813 with a pressure source, e.g. a pressure vessel 814, through a second enclosed space 815 in said crankshaft 800 (axel 801), so that said piston 806 is being pressurized by a fluid 822, said piston 806 will begin to move from a second longitudinal position to a first longitudinal piston position, thereby rotating said U-shaped axel 801 around the bearings 802 and 803. Said movement will change the direction of the movement of said piston 806 into an opposite direction, namely from a first to a second longitudinal piston position. The enclosed space 813 of said piston 806 may then be communicating with a third enclosed space 816 in said crankshaft 800 (axel 801), which is connected through a channel [817] to a piston pump 818 (which may also be instead a rotation pump, e.g. a centrifugal pump), which is connected by a piston rod 819 to a crankshaft 820, with the U-shape axel 821. The crankshaft 820 may be connected to crankshaft 800, so that the rotation of the U-shaped axle 801 results in a rotation of said U-shaped axle 821 with contraweights 834. Due to said communication is the pressure of the fluid 823 inside said piston 806 be reduced, thus is the circumference of the wall 808 decreased, so that said piston 806 is being able to move from first to second longitudinal piston positions. The fluid 823 is at a reduced pressure (in relation to the pressure of the fluid 822 it had, when the piston was pressurized at a first longitudinal position) is thereafter pressurized by said pump 818 to fluid 827 (of which pressure is of course still less than the pressure of fluid 822) and which is optionally directly transported to said pressure vessel 814 through channel [824], or is preferably transported by channel [825] to another piston pump 826, whereafter said fluid 827 is being pressurized in said pump 826 into fluid 822, and thereafter transported through channel [828] to pressure vessel 814. It may also be possible to repressurize said pressure storage vessel, 814, through a hose 2701, which is communicating with a pressure source. From pressure vessel 814 is fluid 822 transported to the second enclosed space 815, through channel [829]. Piston pump 826 is electrically driven by motor 830 through another crankshaft 831. Said motor 830 may be connected by a wire [1069] with an electrical storage, e.g. an accumulator (or a condensator ('capacitator') storage type) 832, which is connected to a solar cell 833. The electric motor 830 is capable of being used as a starting motor for the rotation of said crankshaft 800. This may be done by a clutch 836 (not shown). The crankshaft 800 may be connected to a flywheel 835 (not shown), and a gearbox 837 (not shown) - said gearbox 837 may be using Fluid Dynamic Bearings in order to reduce friction. The bearings 833 for the crankshaft 821 of the piston pump 818. The alternator 850 is communicating with the main axle 852, and is charging the battery 832 through connection 842.The configuration 851 of auxilliarly power sources is shown in Figs. 15 A, 15B , 15C or 15E. It may also be that this battery 832 is charged by an external electrical power source 2700 through e.g. a cable.

Fig. 1 IB shows schematically the control devices for the motor of Fig. 1 1 A. The electric starter motor 830 is comprising a clutch (not shown), connecting the axle 831 and/or 852 with the anker of the electric motor, when the motor needs to be started. An electric switch 838 can turn said starter motor 830 on and off, by connecting it to the battery ('accumulator') 832, which is being loaded by the solar cells 833. Said motor 830 will also be able to be stopped, when the pressure in the pressure vessel 814 meets a certain maximum limit, and said pressure measurement is being done by a pressure sensor 839.

The motor may also start without using the starter motor 830, but just by opening up the reduction valve 840, in the channel [829]. Opening this reduction valve 840 more up causes the crankshaft 801 to rotate more quickly, screwing the reduction valve 840 down causes the crankshaft 801 to rotate slower. Closing the reduction valve 840 completely will stop the motor. The speeder 841 is communicating with the reduction valve 840. The alternator 850 is communicating with the main axle 852, and is charging the battery 832 through connection 842. The configuration 851 of auxilliarly power sources is shown in Figs. ISA, 15B , 15C or 15E. Figs. 11A-F (incl.) concern motor with an elongate cylinder and a piston communicating with a crankshaft, according to the Consumption Technology. Fig. l lC shows the actuator piston pressure management of Figs. 11A and 1 IB. At the point of time when the piston has arrived from a 1st longitudinal position at the final 2^nd longitudinal position of the chamber - thus just after having reversed the direction of its motion - there starts a communication between the high pressurized second enclosed space 822 of said crankshaft, through a hole in said crankshaft and a hole at the end of said piston rod with the enclosed space of said piston rod and thereby also with the internal volume of the piston through hole 1101, so that the piston pressurizes to the maximum pressure rate. Due to its pressuration will the piston beginning to move to a 1^st longitudinal position, thereby turning the crankshaft and closing said hole, so that said communication stops. Said movement is reducing its internal pressure due to its increased inside volume, due to the fact that the ellipsoide shaped piston is beginning to transform itself into the shape of a sphere. When having arrived at the 1^st longitudinal position there is still a medium rate of pressure left in said piston and the enclosed space within the piston rod. When said piston has arrived at the primo 1^st longitudinal position on its way back to a 2^nd longitudinal position - thus just after having reversed the direction of its motion, the enclosed space within the piston rod will begin to communicate through a hole 1102 at the end of the piston rod, and with the third enclosed space 823 within the crankshaft which is comprising a hole. The pressure inside the piston and the enclosed space drops to a certain minimum (e.g. atmospheric level), so that the shape of the piston is changing from a sphere to an ellipsoide. Due to the inertia of the crankshaft (or the driving force of another piston-chamber combination using the same crankshaft) the deflated piston will move to a second longitudinal position, and the process starts all over again.

The communications between the enclosed space of said actuator piston and the second and third enclosed spaces, respectively in the crankshaft may make that said piston may have to stop at a certain longitudinal position, in order to be able to move again, just by opening up the reduction valve, as the pressurized fluid needs to be able to reach the piston. That may only be a problem, when there is only one actuator piston-chamber combination on a crankshaft on one axle, where the piston may stop at a 1^st longitudinal position, and may be returning a bit on its way to a second longitudinal position due to inertia. Said holes of said enclosed spaces may than not be able to communicate with each other - starting may than only be possible by using a starter motor.

The pressure drop in the piston may be caused by a suction in the third enclosed space 823, caused by the piston pump 818, being taking in fluid from channel [817]. The pressure drop in channel [817] may begin to happen a bit before the actuator piston is reversing its direction of motion from being approaching a 1^st longitudinal position to a second longitudinal position, so that when said holes of the enclosed space and the third enclosed space open up, the fluid may be sucked out of said enclosed space of the actuator piston. That means that the default angle between the crankshaft 801 of the actuator piston 810 and the crankshaft 821 of the piston pump 818 may be different from zero. The main axle 852.

Details of the assembly of the piston rod 805 and the U-bend axle 801 are shown in Fig. 11D. Details of the joint of the piston rod 805 and the connecting rod 925 are shown in Fig. HE. Details of the assembly of the piston rod 819 of the pump 818 with the crankshaft 820 are shown in Fig. l l.T. Details of the guidance of the connecting rod 925 and the piston rod 819 may be seen in section 19597 of this patent application.

As another preferred detail: there may be a combined assembly comprising two check valves with each a valve actuator according to preferably Fig. 21 OF or optionally Fig. 210E from the 2^nd enclosed space 822 of the crankshaft 800 to the space 813 of the piston rod 805 and the same assembly comprising a check valve with a valve actuator according to preferably Fig. 21 OF or optionally Fig. 210E from the space 813 of the piston rod 805 to the third enclosed space 823. It may also be two separate assemblies, each comprising a check valve 522 with a sub-assembly 520 comprising a valve actuator according to Figs. 304 and 301 : one from the 2^nd enlosed space 822 of the crankshaft 800 to the space 813 of the piston rod 805 and the same assembly in opposite direction comprising a check valve 522 with a sub-assembly 520 comprising a valve actuator according to Figs. 304 and 301 from the space 813 of the piston rod 805 to the third enclosed space 823.

Fig. 1 ID shows the assembly of the piston rod 805 and the U-bend axle 801 of Fig. 11C, and is shown on a certain point of time, where the piston rod 805 and the U-bend axle 801 are turning over each other. The U-bend axle 801 on which the piston rod 805 has been assembled with a bearing 1100, 1100' and 1100", and the O-rings 1104, 1104'_» 1104" and 1 104'" between the piston rod 805 and the axle 801. The enclosed space 813 is communicating with the third enclosed space 816 (with fluid 823) through (currently) hole 1 102. The second enclosed space 815 with fluid 822 is communicating with current blind hole 1 101, and is thus currently not communicating with the enclosed space 813. The separator 1103, which is separating the second enclosed space 815 and the third enclosed space 816. At another point of time is the current hole 1 102 becomes a blind hole, while the current blind hole 1101 has become a hole. Said holes 1101 and 1 102 are never commnicating with the enclosed space 813 at the same time. The base 926 of the piston rod 805 is comprising two parts 927 and 928, where the centre axis 929 of the channels 822 and 823 are lying in the separation surface (not shown) of said base 926. Two bolts 930 and rings 931 on each side of the piston rod 805 are holding the two parts 927 and 928 together. Fig. HE shows a detail of the joint of the piston rod 805 and the connecting rod 925 (805'), shown in Fig. 11C. Piston rod 805 is having an end 932, which is comprising a channel 933 which is communicating with the 2^nd enclosed space 815 and the 3^rd enclosed space 816 on one side, and the other side to the enclosed space 813 of the piston 810. Both enclosed spaces are communicating with each other through a space 941, between the hole 945 in the outer wall 943 of the end 932 of the piston rod 805, and the hole 946 in the inner wall 944 of the connecting rod 925. The end 942 of the connecting rod 925 is comprising an O-ring 939, which is sealing said end 942 to the said end 932 of said piston rod 925. Axle 940 is firmly connected (not moving) into said end 932. The end 932 of the piston rod 805 is comprising of two parts 934 and 935, which are bolted together by bolt 936 and washer 937 one on each side of the center line 938 of the assembly. The connecting rod 925 can turn over the end 947 of said axle 940. Said end 947 has a increased diameter in relation to the diameter of the axle 940, in order to create a shoulder 953. The parts 934 and 935 of the end 925 have a 90° bearing 948 which is also the bearing for the movement of the end 942 over the end 932. The O-ring 950 is sealing the axle 940 on the hole 947 of said connecting rod 925. Fig. 1 IF shows a detail of the U-shaped axle 801, and a channel (e.g. 823) inside said crankshaft, which is shown in Figs. 11A-C. The channel 823 may be drilled out, after a preliminary hole has been made by forgery, during the production process of the crankshaft 801. This drilling leaves holes in the outer walls 952 of the crankshaft 801, and these holes may be closed by any means, such as welded rods, sealed threads etc. Shown in the drawing is a pin 954 with a head 955, the pin having a very fine fit to the hole in the wall of the crankshaft, where the in between space is being filled by hard soldering. Important is the proper balancing of the crankshaft 801 at the end of the production process.

Figs. 1 1G-W (incl.) concern a motor with at least one elongate cylinder and a piston communicating with a crankshaft, according to the Enclosed Space Volume Technology (abbreviated by "ESVT").

Figs. 11G and 1 1H show the basic ESVT in two variants, regarding the pressurizing of a storage pressure vessel, where the pumps which are controlling the volume of the enclosed space, are driven by a 2-way actuator. Clearly are the different power lines shown, separating the use of the power, generated by the auxilliarly power sources.

Fig. 1 1G shows schematically a configuration of Fig.11 A, adapted to the ESV-Technology, with the U-shaped axle 80 comprising two counterweights 804, the piston rod 805 and the inflatable actuator piston 806. One end of said axle 80 may be connected to an electric starter motor 830, which may get its energy from an accumulator 832 - the last mentioned may be loaded by a solar cell 833, and/or any other preferably sustainable (or optionally non-sustainable) power source (please see Figs. 15A-F). At the other end may the axle 80 Γ be connected to a flywheel 835 (not shown), a clutch 836 (not shown), and optionally a gearbox 837 (not shown).

Inside said U-shaped axle 801 ' is a channel 1050 which is communicating constantly with an

ESVT pumpl055, comprising a piston 1061 (e.g. shown according to Figs. 50-52 (incl.)), and a conical chamber 1062, which is regulating the extra pressure upon the overall pressure in said channel 1050. Said extra pressure is controlling the speed of the motor. The motion of said ESVT-pump 1055 is generated by a 2-way actuator 1053, which is controlled by two reduction valves 1057 and 1058, respectively, where each reduction valve is regulating the pressure at one side of the piston (not shown) inside said 2-way regulator 1053. Reduction valve 1057 is communicating by channel 3300 with one side of 2-way actuator 1053, and reduction valve 1058 communicates by channel 3301 with the other side of 2-way actuator 1053. Said reduction valves 1057 and 1058 are interconnected preferably electrically (and optionally mechanically - other solutions exist but are not shown), so that an increase of the pressure of one (side of said piston) will result in a simultaneously decrease of pressure of the other (side of said piston) and vice versa. Reduction valve 1057 is controlled by a speeder 841, through a control device 840'. Said reduction valves 1057 and 1058 are communicating with a pressure storage vessel 890, through a feeder line [829]. Said pressure storage vessel 890 may have been pressurized with a fluid 1063 when this motor was produced.

Said channel 1050 is additionally constantly communicating with the piston rod 805 of an ESVT- pump 1056 - please see Fig. 1 IT for details of the assembly of said connection rod with the axle 801 '. Thus, a change in the volume/pressure of said ESVT-pump may be resulting in a change of the volume/pressure in the actuator piston 806 and thus in the motion of said actuator piston 806.

The ESVT pump 1056, comprising a piston 1059 (e.g. shown according to Figs. 50-52 (incl.)), and a conical chamber 1060 is driven by a 2-way actuator 1072 regulates the pressure of the channel by changing the volume of said channel, so that the actuator piston 806 is changing volume at a certain longitudinal position, according to Figs. 10A-F. Said 2-way actuator 1072 is driven by the reduction valves 1051 and 1052 in the same way as the ESVT-pump 1055 by 2-way actuator 1053. However, the reduction valve 1051 is being controled by a sensor 1064 and communicates [1054] the rotational position of the axle 801 to said reduction valve 1051, so that the piston 806 may be expanding and contracting at the right point of time, due to the pressure change. The reduction valves 1051 and 1052 may be communicating [829] with a pressure source, e.g. said pressure storage vessel 890. The other side of the enclosed space may be communicating constantly with the enclosed space 813 of the piston 806. Said reduction valves and related equipment are electrically communicating through wire [1069] with the battery 832.

Fig. 11H shows the configuration of Fig. 11G (with components with references for which is referred to Fig. 11G), where the pump 826 for repressuration of the pressure storage vessel 890 has been added - the repressuration cascade is identical with that shown in Fig. 11 A, however, the pump 820 may be redundant, because it may be needed for the 'Consumption Technology', providing a low pressure in the 3^rd enclosed space, at the right point of time, enabling depressurization of the actuator piston 806, but may not needed for the currently used ESV Technology. The outlet [1070] of the 2-way actuator 1072 is communicating with the pump 820, but can be connected to the feederline [825] of the piston pump 826, when the pump 820 is not present. The necessary check valves are not shown. In this ('consumption') configuration of the 2-way actuators 1053 and 1072 are the spaces at both sides of the piston inside the chamber of the 2-way actuators, directly communicating with the pump 826, which is communicating with the pressure storage vessel 890, and with the reduction valves 1051, 1052, 1057 and 1058 respectively, which then are communicating with the inlets of said 2-way actuators 1053 and 1072, respectively, to the spaces at both sides of said piston (please see Fig. 1 1 for a schematic view inside the 2-way actuator 1053'). The necessary check valves are not shown. Said reduction valves 1057-1058 and 1051-1052, respectively, are related to each other, in such a way that if one valve is being opened more, the other valve is simultaneously closing more. The valve means 840' of the reduction valve 1057 is being activated by a speeder 841, while the reduction valve 1051 is activated by sensor 1064 with communication [1054]. The reduction valves are being electrically activated through wire [1069].

The alternator 850 is communicating with the main axle 852, and is charging the battery 832 through connection [842]. The configuration 851 of other auxilliarly power sources is shown in Figs. 15 A, 15B, 15C, 15E or 15F. The pump 826 may also communicating with a flywheel (not shown) and/or a regenerative breaking system (not shown). The use of other auxilliarly power sources is possible, as stated in the drawing: preferably according to Figs. 15A, 15B, 15C, 15 E, 15F and optionally non-sustainable power sources.

Figs. I ll - UN (incl.) show a one (Figs. I ll, UK, 1 1M) and a two cylinder motor (Fig. 11 J, 1 1L, UN), respectively, where said motors have been partially worked out for the main construction elements (e.g. axles and e.g. wheels and belts / gears), which are communicating with each other. The ESVT pump, which is controlling the volume of the enclosed space is powered by a 2-way actuator (Figs. 1 11, 11 J) according to the configuration shown in Fig. 1 1H, a crankshaft (Figs. UK, 1 1 L) or a camshaft (Figs. 11M, UN), respectively. Due to the different sizes of the loops of said power types, the conical cylinders may have different sizes per each power type. The auxiliarly power sources are only referred to by reference number. The use of other auxilliarly power sources is possible, as stated in the drawing: preferably according to Figs. 15 A, 15B, 15C, 15 E, 15F and optionally non-sustainable power sources.

Each drawing which is comprising a two cylinder motor is consisting of a "left" and a "right" scaled up drawing.

Figs. I ll - 1 1R (incl.) show several configurations of a one cylinder motor, and a two cylinder motor. One of the aims is to show the clear updividing of the power delivered, and the power used - this has been also disclosed schematically in Figs.15. Another aim is to show the differences between controlling the pressure rebuild of the actuator piston(s) by either wires, by a camshaft or by a crankshaft which may be communicating to the power delivered. In order to enhance the efficiency of the power delivered, Figs, l lo - 1 1R show a small combustion motor, using preferably ¾ as power source (preferably derived from hydrolyses of H₂0), which is directly communicating with a camshaft or a crankshaft. Several configurations are being shown of this combustion motor. Another aim is to show how the controlling means of the pressure per cylinder, may be combined or not in a more than one cylinder motor - it showed to be necessary to find out firstly how the subsequent cylinders would be working in relation to each other, under condition of a combined crankshaft: please see Figs. 17A,B-H (incl.) where the power strokes of one of the two cylinders of the same motor is done simultaneously with the return stroke of the other cylinder (serial power), while in Figs. 18A-G (incl.) the power strokes of the two cylinders of the same motor are functionning at the same time (parallel power). Thereafter, it is concluded which pressure controlling means (e.g. ESTV pumps) may be combined for said 2 cylinders or not, and whether or not the power lines (e.g. camshaft, crankshaft) may be combined. Fig. 1 II is showing a partially worked out one piston-chamber combination 800' motor, which is mainly based on the concept -shown in Fig. 1 1H, using a 2-way actuator 1072 to drive the ESVT-pump 1056, which is controlling the size of the enclosed space 1050 + 813, and is functioning as described in Fig. 11H. The actuator 1055 (piston 1061 , chamber 1062) is controlling the speed of said motor. All remarks regarding the presence or not of the pump 820 made in the description of Fig. 1 1H are also valid here.

Only new issues will be treated here.

Please see Fig. 1 IS for the details of the assembly of said actuator 1055 onto said axle 852. The top 1130 of the chamber 1062 of the actuator 1055 has been mounted on the motor mainframe 5000. The arrangement of the communication between the enclosed space 1050 of the axle 852 and the chamber 1062 can be seen in Fig.1 1 S as well.

The actuator 1053' which is changing the speed of said motor has been partially worked out, and is working in a bit different way than the actuator 1053 shown in Fig. 1 1H, because said actuators 1053 and 1072 have different functions. In the configuration shown in this drawing of the actuator 1053' are the spaces 1075 and 1076, respectively on both sides of the piston 1078, within said chamber 1079, communicating with each other through a number of check valves (not shown here) - please see Figs. 16A-C (incl.) for details. Thus, there is no return flow from said spaces 1075 and 1076 through a pump 826 to the pressure storage vessel 890. This may reduce energy.

Said spaces 1075 and 1076, respectively are communicating with said reduction valves 1058 and 1057, respectively. Said chambers are additionally communicating with each other through valve actuator arrangements 1121 and 1 122, respectively, shown in Fig. 304, and when necessary may these additionally be controlled according to Figs. 2 HE or 21 IF. Said valve actuator arrangements 1121 and 1122 are being positioned in opposite direction to each other. The chamber 1079 of the actuator 1053' has been mounted on the motor mainframe 5000. More details are shown in Figs. 16A-B.

The ESVT-pump 1056 is comprising a chamber 1060 and a piston 1059, has been mounted on the main axle 852 - please see Fig. 11U for suspension details. Said 2-way actuators 1053 and 1072 are driven by a compressed fluid 1063, which has been stored in a pressure storage vessel 890. Reduction valve 1051 is activated by communication line [1054] and powerline [1069] through electric regulator 1065.

The pump 826 of Fig. 1 1H has been worked out in detail in Fig. 11V. It gets its energy from an electric motor 830', which receive electricity through an electric communication [1080] from a battery 832. The circular movement ^"of the axle of said motor 830', is being conversed by a kind of crankshaft 1217 to a translation, and partially a rotation. When the pump 820 is not present, will the flow from the 2- way actuator 1072 be communicating by channel [1083] to said pump 826. Compressed fluid is coming from said pump 826 through channel [828] to the pressure storage vessel 890. The alternator 850 is communicating with the main axle 852 through a tooth belt 1073 and wheels 1074 and 1077. It delivers electric power to the battery 832, through the electric communication 842. Electrical drive system 830 is similar to said elements of Fig 1 1A.

Fig. 1 1J is showing an overview of a two cylinder motor, while particulars are shown in the scaled up Figs. 1 1J left and 1 1J right.

Fig. 11 J is showing a partially worked out two cylinder motor, based on the concept shown in Fig. 111. Particulars are shown when combining two crankshafts, and having the benefit of one construction element for multiple sunilar tasks. In a two cylinder motor are there not many of the last mentioned, because of showing here an example, where the two actuator pistons may not be in the same longitudinal position, at the same moment (asynchrone crankshaft design) according to Fig. 17B. Each "cylinder", better designated as 'chamber' has an enclosed space comprised in its crankshaft, hereinafter designated as 'sub-crankshaft', which have been separated from each other by e.g. a tightening rod 1270 (Fig.1 IX) in between the channels of each sub-crankshaft.

Thus each actuator piston has an ESVT-pump controlling the volume of each enclosed space, while each ESVT-pump is ^"driven by a 2-way actuator. As the actuator pistons have to be moving (a)synchrone, may it be necessary that the pressure reduction valves of each 2-way-actuator are communicating with each other 1066 for synchronisation purposes, e.g. electrically. However, it may also be that said pressure reduction valves are communicating through the sub-crankshafts, each by its sensor measuring the rotation of each sub-crankshaft 1064. Whether or not the two ESVT-pumps may be combined into one, cannot be concluded without substantial investigations: please see Fig. 17C-17H (incl.).

And, thus there are two speeder-actuators, which have to be communicating with each other 1067. This may be done through the speeder 841 - one speeder, which is controlling e.g. electrically both pressure reduction valves of each 2-way actuator 1057. Whether or not the two 2-way actuators may be combined into one, cannot be concluded without substantial investigations: please see Fig. 17C-17H (incl.).

There may be two or only one pressure storage vessel, which has been pressurized Ex. Works, and which is being repressurized during operation by a pump. It may possible that there is one pump, which may be driven by electricity from a battery 832, which has been charged Ex. Works, may be recharged during operation by an alternator 850, communicating with the main motor axle 852. It may also be possible that this battery is charged by an external electrical power source through e.g. a cable. It may be possible to repressurize said pressure storage vessel 890 through a hose, which is communicating with a pressure source, such as preferably a medium pressure canister or optionally a high pressure canister, or an external pump (e.g. driven by a windmill - most efficient). Auxilliarly power sources are according Figs. 15A,B,C,E,F, of which at least one may charge said batteries.

Firstly when there are 3, or better 4 and even pairs over 4 cylinders in one motor, will there be a chance to combine the inlet/outlet of 2-way actuators for speed control, and the inlet/outlet of ESTV- pumps, so that the total number of said 2-way actuators and pumps may be reduced. Please see Figs. 17C- 17H (incl.).

The pump 820 may be redundant.

The two sub-crankshafts on the main motor axle are connected to each other, by a connector of which details are shown in Figs. 1 1W, 1 1W, 1 IX, which may be a little bit flexible in a plane perpendicular that of the centre axis of said crankshaft, in order to compensate for a possible timing difference of the changes of shapes of said actuator pistons, due to elastic characteristics of the wall of said actuator pistons during repressuration.

Fig. 11 J left shows a scaled up of the left part of Fig. 1 1 J.

Fig. 1 1J right shows a scaled up of the right part of Fig. 1 1J.

Fig. 1 IK is showing a one cylinder motor, which is based on the concept shown in Fig. 11H, where instead of a 2-way actuator, an auxilliarly crankshaft is used to drive the ESVT-pump. Said auxilliarly crankshaft is driven by an electric motor, which is powered by said battery. Said battery is recharged during operation by an alternator, which is communicating with the main motor axle. Due to the need for co-ordinating the speed of the speed-actuator with the speed of said ESVT-pump, the controls of both: the speeder 841, pressure reduction valve 1057 and said electric motor 3500 are communicating with each other by wire [3501] through an electric/electronic regulator 3502. The motor 3500, also shown in the following Figures 1 1L, 11M and UN, is driving the crankshaft 3503 through e.g. a toothbelt 3505 and wheels 3506 and 3507., which is driving the ESVT pump 1056. Said electric motor 3500 is connected to the battery 832 by wire [3504], through said regulator 3502.

The fact that a (auxilliarly) crankshaft is used for driving the ESVT-pump, which is mounted on a fixed crankshaft axle, there may be a connecting rod, which connects the piston rod of the ESVT-pump with the crankshaft (as we have seen in Figs. 1 1C for the actuator piston) or that said connecting rod is missing, and that a similar the oscillation construction of the pump shown in Fig. 1 IV is being used, where the chamber 1060 of said ESVT-pump, incl. the top 1 130 and the piston rod are turning around said crankshaft which is communicating with said main axle 852. The assembly of the ESVT-pump on the main axle is as such the same as if the pump was not oscillating (e.g. see Fig. 11U, but the fits of the bottom of said pump to the axle may be slightly bigger.

Because the 2-way actuator 1072 of the ESVT-pump has been exchanged by an auxilliarly crankshaft, and the fact that the 2-way actuator 1053 may not need repressuration, rather than keeping the pressure storage vessel pressurized, which may demand a limited repressuration, the pump 826 may be smaller than the one shown in Fig 1 11. This is a preferred solution, while a solution of having a pump 820, while pump 826 has been redundant is an optional solution.

Fig. 11L is showing an overview of a two cylinder motor, while particulars are shown in the scaled up Figs. 11L left and 1 1L right.

Fig. 1 1L is showing a two cylinder motor, based on the concept shown in Fig. UK, where each cylinder has an enclosed space, and thus an ESVT- pump controlling its volume each, which both are driven by the same auxilliarly crankshaft axle.

Due to the need for co-ordinating the speed of the speed-actuators with the speed of said ESVT- pumps, the controls of both: the speeders 841 / pressure reductions valve 1057 and the electric motor 3500 are communicating with each other, when both ESVT-pumps are using the same axle comprising both crankshafts.

Because the 2-way actuator 1072 of the ESVT-pump has been exchanged by an auxilliarly crankshaft - this may be made as one piece due to the fact that the assembly of the connection rod and the crankshaft is simple (no channel) - and the fact that the 2- way actuator 1053 may not need repressuration, rather than keeping the pressure storage vessel pressurized, which may demand a limited repressuration, the pump 826 may be smaller than the one shown in Fig 1 11. This is a preferred solution for a two cylinder motor, while a solution of having a pump 826, while pump 820 may be no option.

Fig. 11L left shows a scaled up of the left part of Fig 1 1 L. Fig. 11L right shows a scaled up of the right part of Fig 11 L. Fig. 11M is showing a one cylinder motor, which is based on the concept shown in Fig. 11H, using a camshaft to drive the ESVT-pump, instead of the 2-way actuator.

Said camshaft is driven by an electric motor, which is powered by said battery. Said battery is recharged during operation by an alternator, which is communicating with the main motor axle. Due to the need for co-ordinating the speed of the speed-actuator with the speed of said ESVT-pump, the controls of both: the speeder 841 , pressure reduction valve 1057 and said electric motor 3500 are communicating with each other, in the same way as shown in Fig. 11 K.

The camshaft 3515 has a limited height of the cam 3516 to lift the piston rod of the ESVT- pumpl056, and that means that the ESVT-pump has a decreased stroke length, and an increased width of aid chamber than that of Figs. UK and 11L, in order to obtain the necessary change of volume. Additionally may a spring be needed, to let the piston reverse its motion, which had been initiated by a cam.

Because the 2-way actuator 1072 of the ESVT-pump has been exchanged by an auxilliarly camshaft, and the fact that the 2-way actuator 1053 may not need repressuration, rather than keeping the pressure storage vessel pressurized, which may demand a limited repressuration, the pump 826 may be smaller than the one shown in Fig 1 II. This is a preferred solution, while a solution of having a pump 820, while pump 826 has been redundant is an optional solution.

Fig. 1 IN is showing an overview of a two cylinder motor, while particulars are shown in the scaled up Figs. 1 IN left and 1 IN right. Fig. UN is showing a two cylinder motor, based on the concept shown in Fig. 11M, where each cylinder has an enclosed space, and thus a pump controlling its volume, which both are driven by the same camshaft.

Due to the need for co-ordinating the speed of the speed-actuators with the speed of said ESVT- pumps, the controls of both: the speeders 841 / pressure reductions valve 1057 and the electric motor 3500 are communicating with each other by wire [3501] through an electronic/electric regulator 3502, when both ESVT-pumps are using the same camshaft axle.

Because the 2-way actuator 1072 of the ESVT-pumps have been exchanged by a camshaft, and the fact that the 2-way actuator 1053 may not need repressuration, rather than keeping the pressure storage vessel pressurized, which may demand a limited repressuration, the pump 826 may be smaller than the one shown in Fig 111. This is a preferred solution for a two cylinder motor, while a solution of having a pump 826, while pump 820 may be no option.

Fig. 1 IN left shows a scaled up of the left part of Fig 1 IN.

Fig. 1 IN right shows a scaled up of the right part of Fig 1 1 N.

Figs. Ι ΙΟ,Ρ and 11Q,R (incl.), respectively concern the configurations of Figs. 11K,L (crankshaft) and Figs. Ι ΙΜ,Ν (camshaft), respectively, where the auxilliarly power source is, besides the solar cells 833, a configuration according to Fig.l5C, where a combustion motor 3525, preferably using H₂ (and optionally any other combustible power source), which has been preferably generated by electrolyses from conductive H₂0 (and from a canister under pressure - cooled and liquified or not), is directly communicating with the ESVT pump which is controlling the volume of the enclosed space. Instead of the configuration in Fig 15C different configurations, such as the configuration of Fig 15D, may be used. The fact that said combustion motor directly drives the power lines (ESVT-pump(s), crankshaft/camshaft, instead of first generating electricity, which drives an electric motor, means that it is approximately 4 times more efficient. Each drawing shows a different type of cooling for said combustion motor. The by said combustion motor heated fluid (e.g. air) may be used for heating purposes, e.g. for heating the compartment of a car. Fig. HO is showing a one cylinder motor, based on the above mentioned concepts, using a crankshaft for driving the ESVT pump. Only new issues are treated here.

In order to get said motor running properly it is necessary to synchronize the several parts in said motor:

· the electrolyses of H₂o which results in a certain volume of H₂ and O2 to be used for the combustion motor, driving the crankshaft, driving the ESVT-pump,

• the communication between the ESVT-pump and the 2-way actuator for the speed actuator has been treated in the description of Figs. 1 I K, 1 1 L, 1 1 M and 1 IN. the motor is also driving the pump 826 shown in Fig. 1 1V, for repressuration of the pressure storage vessel 890, through a tooth belt and wheels

The configuration (according Fig. 15C) of the auxilliarly H₂ combustion motor is comprising a storage tank 1612 for conductive H₂0 1613 (which may be H₂0 from the tap and a conductor, e.g. salt, or just sea water), with a filler opening 1614 and an outlet channel [1615] to the vessel 1616 wherein the electrolyses 1617 of said water 1613 is taking place. Wire [3547] is connecting the speeder 841 with a regulator 3509, controlling the production level of H₂ and 0₂ through electrolyses. No check valves have been shown. The electric power line [3547] from the battery 832 to the vessel wherein the electrolyses is taking place. The resulting H₂ is transported [3545] by a pump to said motor - the very necessary check valves have not been shown. The resulting 0₂ is being transported [3546] to said motor as well by channel + pump - the very necessary check valves are not shown - it is used as a kind of turbo. Said H₂ motor 3525 is shown in this drawing as being air cooled, where the warm air is being transported through a channel [3538], directly or indirectly by a liquid to a heat exchanger 3539, e.g. for warming up (arrows 3540) purposes of the cabin of a car.

Fig. I IP is showing an overview of a two cylinder motor, while particulars are shown in the scaled up Figs. I I P left and 1 I P right.

Fig. I IP is showing a two cylinder motor, based on the concept shown in Fig. 1 10, where each cylinder has an enclosed space, and thus an ESVT- pump, which both are driven by the same crankshaft, and two speeder actuators, but one auxilliarly motor. The crankshaft is directly driven through gear wheels 3526 by a liquid cooled combustion motor, using H₂, derived by the electrolyses of H₂0. Said crankshaft is driving the ESVT-pumps, and the pump 826 which is repressurating the pressure storage vessel 890. The shown toothed belt 3527 may be exchanged by gear wheels.

There is a water pump 3528 for circulation of the cooling water 3529 from the air cooled radiator 3530, and to another radiator 3531, which may warm up air from the surroundings for warming up e.g. the cabin of a car. Said water pump is communicating with the main axle 852 of said motor, as well as the alternator 850, which is recharging the battery 832. Fig. 1 IP left shows a scaled up of the left part of Fig I I P.

Fig. 1 IP right shows a scaled up of the right part of Fig 11 P.

Fig. HQ is showing a one cylinder motor, based on the above mentioned concepts, using a camshaft for driving the ESVT pump. The principle of the camshaft in Fig HQ is equal to that of Fig 11M. The camshaft is is directly driven by the auxilliarly power from a forced gas (e.g. air) cooled combustion motor. The pump, which is repressurising the pressure storage vessel, is directly driven by said combustion motor. The batteries 832 are being charged by an alternator, which is mounted on the main motor axle, or according to Fig 15.D.

Fig. HR is showing an overview of a two cylinder motor, while particulars are shown in the scaled up Figs. 1 1R left and 1 1R right.

Fig. 11R is showing a two cylinder motor, based on the concept shown in Fig. HQ, where each cylinder has an enclosed space, and each an ESVT-pump controlling its volume, which both are driven by the same camshaft. The whole concept is know from earlier drawings.

Fig. 1 1R left shows a scaled up of the left part of Fig 1 1 R. Fig. 11R right shows a scaled up of the right part of Fig 11 R.

Figs. 11 S-W (incl.) show specifics of several construction elements, which has been used in the Figs. 11A-R (incl.).

Fig. 1 1 S shows a detail of the joint of the pump 1061 of the piston-chamber combination according to Figs. I ll - 1 1 R with the main axle 852 of the motor, using the ESV Technology. The base

1140 of the pump 1061 is comprising two base parts 1141 and 1 142, which have been bolted together by two bolts 1143 and washer 1144, around the main axle 852 with an appropriate fine fit. Said base part

1141 is bolted on the motor housing 1 145, which has a bearing 1 146 around the main axle 852, which is turning around. Said motor housing is shown as a hatch 5000. The base parts 1141 and 1 142 have an O- ring 1148, which is sealing the sliding connection between the main axle 852 and the base parts 1141 and 1142. The pump chamber 1149 is communicating with the 3^rd enclosed space 1150. The bolt 1151 and the washer 1152.

Fig. 1 IT shows a detail of the joint of the connecting rod 805' of the actuator piston 806 and the crankshaft 801 'on the main axle 852 of the motor according to Figs. 1 1G - 1 1R, using a continuous communication between the enclosed space 813 of the actuator piston 806 and the channel 1050 of the crankshaft 801 ', due to the use of the ESV Technology.

The assembly of the connecting rod 805' and the U-bend axle 801 ' of Figs. 1 1G - 11R is shown, on a certain point of time. The connecting rod 805' and the U-bend axle 80 Γ are turning over each other. The U-bend axle 801 ' on which the connecting rod 805' has been assembled with bearings 1 100 and 1100", and the O-rings 1104 and 1104"' between the connecting rod 805' and the axle 801 '. The enclosed space 813 is communicating with the channel 1050, through the holes 1106, 1 107 and 1 108. There are a few holes, on a certain distance from each other, on different circular places on the circumference of said axle 801 ', in order to avoid stress in the axle 80Γ. The channel 1050 is constantly communicating with the holes 1 106, 1 107 and 1 108 through the open space 1105 and 1105' with the enclosed space 813. It results in a constant communication between the channel 1050 and the enclosed space 813 of the actuator piston 806. The base 926' of the connecting rod 805' is comprising two parts 927' and 928', where the centre axis 929 of the channel 1050 is lying in the separation surface (not shown) of said base 926'. Two bolts 1 1 10 and rings 1 1 1 1 on each side of the piston rod 805' are holding the two parts 927' and 928' together.

Fig. 11U shows a detail of the joint of the pump 1060 of the piston-chamber combination according to Figs. I ll - 1 1 R with the main axle 852 of the motor, using the ESV Technology. The base 1180 of the pump 1060 is comprising two base parts 1 181 and 1 182, which have been bolted together by two bolts 1183 and washer 1184, around the main axle with an appropriate fine fit. Said base part 1181 is bolted on the motor housing 1185, which has a bearing 1186 around the main axle 852, which is turning around. Said motor housing is shown as a hatch 5000. The base parts 1181 and 1182 have an O-ring 1 188, which is sealing the sliding connection between the main axle 852 and the base parts 1181 and 1182. The pump chamber 1189 is communicating with the 2^nd enclosed space 1190. The bolt 1191 and the washer 1192.

Fig. 1 IV shows the mechanism driving a pump, e.g. 826, of Figs. 1 1H - 11R, and its base.

The pump 1200 is comprising a chamber 1201, a wall 1206, a base 1202, and a top 1203 of the chamber 1201. The piston 1204 is of a type described in section 19640 of this patent application, as well as the pressure measuring sensor 1205 at the end of the piston rod 1214. The bearing 1207 in the top 1203 of the pump 1200 is preferably made according section 19597 of this patent application - it means that the bearing 1207 can withstand big side forces from the piston rod 1214. The base 1202 of the pump 1200 can rotate around an axle 1208, within the boundaries 1222 of another base 1209, which is part of the motor housing 1210 - shown as a hatch 1211. On said base 1202, at the opposite side of said axle 1208 than said chamber 1201 of said pump 1200, is a contra weight 1212 assembled, so as to balance the pump 1200 in the centre point 1213 of said axle 1208. The pump 1200 is comprising a piston rod 1214, which is guided by said bearing 1207 in the top 1203 of said pump 1200. At one end of said piston rod 1214 is piston 1204 assembled, while at the other end of said piston rod 1214 is an axle 1216 assembled. Said axle 1216 is positioned perpendicular to the piston rod 1214, and said piston rod 1214 is mounted on said axle 1216. The disk 1217 is comprising a bearing 1218, in which said axle 1216 can rotate, and which is a-centrally positioned on said disk 1217, preferably near the side 1219 of said disk 1217. Said disk 1217 is rotating around a disk axle 1220, which is communicating with an electric motor 1221. The rotation of said axle 1220 is rotating the disk 1217, by that the axle 1216 is a-centrally rotating in a plane perpendicular to said disk 1217, around said axle 1220. This means that the piston rod 1214 is in a translating motion to and from the top 1203 of the pump 1200, while the piston rod 1214 is rotating the chamber 1201 of the pump 1200 from one boundary 1222 to the other and vice versa, within the angles s and t in relation to the centre axis 1223 of said pump 1200. This makes the piston 1204 move in the chamber 1201. The inlet 1224 (not shown) and the outlet 1225 (not shown) of said pump 1200 are part of the base 1202 of said pump 1200, by using said type of piston 1215, and said inlet 1224 and said outlet 1225 may comprise a check valve. The medium 1226 of said pump 1200. The position of the inlet 1224 and outlet 1225 may be different from said positions, when another type of piston is used.

Fig. 1 1W shows the connecting joint between the two crankshafts of the 2-cylinder motor according to Figs. 1 1 J, 11L, UN, I IP, 11R. The shown connecting joint is an improved version of the version shown in the drawings Figs. 1 1J, 1 1L, UN, I IP, 1 1R. In this drawing is the version of this connection joint shown, where the adjacent enclosed spaces are communicating with each other. The crankshaft 1250 of the cylinder left (not shown) is comprising a channel 1251, which is functioning as (2^nd ) enclosed space. It is assembled such that the end 1253 of the crankshaft 1251 is faced to the end 1254 of the crankshaft 1252 of the cylinder right (not shown), wherein between said ends 1253 and 1254 a gasket

1255 is positioned ("embedded") under compression in 3 directions, within the flanges 1256 and 1257, resp. of both crankshaft ends 1253 and 1254, resp. The last mentioned crankshaft 1252 is comprising a channel 1265, which is functioning as (3^rd) enclosed space, and is communicating with the cylinder right (not shown). Each flanges 1256 and 1257 have preferably an uneven number of holes, shown is hole 1258. In said hole is a thin flexible cylinder 1259 mounted with a tight fit with said hole 1258. In said cylinder 1259 is the bolt 1260 positioned with a pass fit. This thin flexible cylinder 1259 enables a very small difference in angle position of the two assembled crankshafts 1250 and 1252, which may arise from dis- synchronisation, due to asynchrone motion of the actuator pistons (not shown). The washer 1261 and the nut 1262.

Fig. 11 W shows an improved (in relation to said gasket 1255) sealing of gasket 1263. The flange

1256 has a cavity 1264, while the flange 1257 has a hump 1265 (not shown), fitting in the cavity 1264. An alternative for the tightening, while the connection is flexible., is shown, where the flange 1257 is flat.

Fig. 11X shows the same as Fig. 1 1W, with the exception that the communication between the channels is not possible, because a tightening rod 1270 has been positioned in the channels 1271 and 1272, of which the common channel parts 1273 and 1274, resp. of each have a larger diameter, in order to obtain a shoulder 1275 and 1276. The tightness of said tightening rod 1270 in one of the channels 1273 or 1274 has been obtained by e.g. an appropriate fit and soldering in one of the ends. The improved sealing of the gasket 1263 - this construction is identical with the one shown in Fig. 1 1 W.

Instead of toothed belts at the power side of the motor according to the Figs.1 ID- W, there where the pump(s) are being driven, may very well be exchanged by gear.

Fig. 12A shows the configuration 800 of the motor according to Fig. 11B, where the piston-chamber combination was communicating through a crankshaft with the main axle, and in this figure has been replaced by a configuration 800', which is comprising a fixed chamber wherein a piston is rotating clockwise according to Fig. 10A or Fig. 12B, and, where the suspension of said piston is shown in Fig. 12C. A 'black box' is shown which is for the entry communicating with a reduction valve 840 through channel [ ], and for the exit communicating with the pump 818 through channel [817]. The reduction valve 840 is being controlled by a speeder 841.

Fig. 12B shows the motor where the piston of an actuator piston-chamber combination is moving, while the chamber is not moving. The motor comprising a chamber 960, which is comprising 4 sub- chambers 961, 962, 963 and 964, respectively, which lie around the same centre axis 965 in continuation of each other, which has an axle 966 through the center 967 of said chamber 960. Within said sub- chambers 961, 962, 963 and 964, respectively is 1 piston 968 positioned, shown on two important positions, namely position 968' when at a l⁵' rotational position of the sub-chamber 964, having the largest diameter, and position 968" when at a 2^nd rotational position of the sub-chamber 961, which is lying in continuation with sub-chamber 964, so that the 1^st rotational position of sub-chamber 964 lies closest to the 2^nd rotational position of sub-chamber 961, where it has its smallest diameter. Said actuator piston 968 is rotating clockwise around said axle 966 - there are shown 4 holes 967 for assembling said chamber 960 on axle 966.

Fig. 12C (consumption) shows the A-A section of Fig. 12B, with the non-movable chamber 960, and movable the piston 968' and 968". The enclosed space 1070 of said piston 968', 968" (the same piston in two different sizes) is ending at the axle 966, where it is sealed with two O-rings 1071, positioned on each side of said enclosed space 1070. The enclosed space 1070 is communicating with a second enclosed space 1072 in the axle 966, where it ends in a housing 1073, where a T-valve 1074' is present, which is controlling the entry of fluid 822 from the pressure storage vessel 814 through channel [829] and reduction valve 840. Said fluid 822 is controlling the presssure inside the piston 968' and 968". The exit from said pistons 968' and 968" is through channel [817] to the cascade of pumps (translational or rotational).

The electrical signal 1076 is communicating with an electrical/electronical control unit 1077, which is controling the T-valve 1074' within the housing 1073 through signal [1078]. The rotation of the axle 966 is thereby controlling said T-valve 1074', and thus the pressure in the piston 968',968". The signal [891] from the pressure source 1075 to the control unit 1077. The flange 1079 is connecting the chamber 960 to the suspension 1080, which is mounted on the axle 966. The belt 1081. A pump as e.g.references 82 and/or 826' of Fig. 13B may be present, but has not yet been showing in this drawing - said pump is communicating with pressure source 1075. Said pump may be communicating with axle 966. It may also be communicating with a flywheel and/or a regenerative breaking system 1082.

Fig. 12D (enclosed space) shows the A-A section of Fig. 12B, with the non-movable chamber

960, and movable the piston 968' and 968". The enclosed space 1070 of said piston 968', 968" is ending at the axle 966, where it is sealed with two O-rings. The enclosed space 1070 is communicating with a second enclosed space 1072 in the axle 966, where it ends in a housing 1073, where a piston-chamber combination 1074 is present, which is controlling the pressure inside the piston 968' and 968"

(the same piston in two different sizes). Said piston-chamber combination may be in connectrion with the fluid 889 of the power source 1075, through channel 890.

The electrical signal [1076] is communicating with an electrical/electronical control unit 1077, which is controling the piston-chamber combination 1074 within the housing 1073 through signal [1078]. The rotation of the axle 966 is thereby controlling said piston-chamber combination 1074, and thus the pressure in the piston 968', 968". The signal [891] from the pressure source 1075 to the control unit 1077. A return channel 1050 with fluid with decreased pressure (to said fluid 889) is returning to the power source 1075, through a cascade repressuration system (translational and/or rotational pumps) (see Fig. 12 A). The 1151.

The flange 1079 is connecting the chamber 960 to the suspension 1080, which is mounted on the axle 966. The belt 1081. A pump as e.g.references 82 P and/or 826' of Fig. 13B may be present, but has not yet been showing in this drawing - said pump is communicating with pressure source 1075. Said pump may be communicating with axle 966. It may also be communicating with a flywheel and/or a regenerative breaking system 1082.

The motor according to Figs. 12A and 12B may comprise a chamber 960 of which, at least a part, may be parallel to the centre axis of said chamber (not shown).

Fig. 13A shows the motor as shown in Fig. 1 1 A, where the crankshaft arrangement 800 has been exchanged by the rotational motor of Fig. 10B.

Fig. 13B shows the motor of Fig. 13 A, wherein the piston pumps 818 and 826 have been exchanged by rotational pumps, e.g. centrifugal pumps: 82 P and 826'. Fig. 13C shows the B-B cross-section of Fig. 13B, and the motor is of a type where the chamber of an actuator piston-chamber combination is moving, and the piston is not moving.

The motor comprising a chamber 860, which is comprising 4 sub-chambers 861, 862, 863 and 864, respectively, which lie around the same centre axis 865 in continuation of each other, which has an axle 866 through the center 867 of said chamber 860. Within said sub-chambers 861, 862, 863 and 864, respectively are 5 pistons 868, 869, 870, 871 and 872, respectively positioned, each at a different rotational position said sub-chambers 8 1, 862, 863 and 864, on an angle a = 72° from each other. Each piston comprising a piston rod 873, 874, 875, 876 and 877, respectively. The pistons 868, 869, 870, 871 and 872 are of a "sphere - sphere" type, and are shown all having different diameters. Said chamber 860 is rotating anti-clockwise around said axle 866 and the sub-chambers 861, 862, 863 and 864 having a second rotational position and a first rotational position in the clockwise rotational direction - there are shown 4 holes 878 for assembling said chamber 860 on axle 866.

Fig. 13D shows the A-A cross-section of Fig. 13C. The chamber 860 having an incision 879 around the flange 861 of said chamber 860, where a belt 883 can be mounted. The chamber 860 has been assembled on said axle 866 which has a flange 880 by a recession. Said piston rods 873, 874, 875, 876 and 877 are assembled inside a housing 882.

Fig. 13E shows cross-section C-C of Fig. 13A, and another cross-section of said housing 882 in view A-A. The piston rods 872, 873, 874, 875, 876 are being connected to a pressure distribution center 884, where each piston is connected to a computer 885 steered reduction valve system 886, that is giving each of the piston rods the necessary pressure - a signal 887 giving the rotational position of said axle 866 to the computer 885 determines by signal 888 the pressures for each of the pistons. The pressure to said piston rods 872, 873, 874, 875, 876 comes through a channel 890 from a pressure

vessel 889, and is controlled by a signal 891 to the computer 885. Both the fluctual pressure change in the enclosed space of each piston is being dealt with separately, but also is the adjustment electronically dealt with for each piston by the same computer 885. A pump (as e.g.references 82Γ and/or 826' of Fig. 13B may be present, but has not yet been showing in this drawing - said pump is communicating with pressure source 1075. Said pump may be communicating with axle 966. It may also be communicating with a flywheel and/or a regenerative breaking system.

Fig. 13F shows schematically an alternative solution for the motor repressurization system, which is now alike that of Fig. 1 IF. Each enclosed space (e.g.1090) of each pistons is communicating with a piston-chamber combination 873, 872,874,876,875, while 873 is comprising an actuator piston 1091 of which its position in the chamber 1092 is controlled by the position of a camwheel 1093, which can turn over a cam 1094, while the cam 1093 is assembled on axle 866. NB: the cam and wheel are shown schematically, as each wheel should have a different distance to its related piston, while the wheel should be shown (partly) sideways. The pressure inside the enclosed space 1090 can be adjusted by another piston chamber combination 1055', which is an analogus of 1055 from Fig. 1 IF, and another controlling actuator 1056' (as 1056) and reduction valves 1057' and 1058' (as 1057, 1058), while additonally the speeder 841 ' (as 841). The pressure vessel 889 ic commincation [1095] with said reduction valves 1057' and 1058'. A pump (as e.g.references 82 and/or 826' of Fig. 13B may be present, but has not yet been showing in this drawing - said pump is communicating with pressure source 1075. Said pump may be communicating with axle 966. It may also be communicating with a flywheel and/or a regenerative breaking system.

The motor according to Figs. 13 A, 13B and 13C may comprise a chamber 860 of which, at least a part, may be parallel to the centre axis of said chamber (not shown).

Fig. 14A shows the change in pressure and size of the actuator piston 1700 positioned in a chamber 1701, having a centre axis 1702, and a piston 1703, mounted on a piston rod 1704 when moving from a 2^nd longitudinal / 2^nd circular position 1705 to a 1^st longitudinal / 1^st circular position 1706. The actuator piston 1700 has been pressurized to e.g. 3½ Bar at said 2^nd longitudinal / 2^nd circular position 1705. Said piston 1700 is comprising an enclosed space 1707, which is comprising a pump part 1708. The pump part 1708 of said enclosed space 1707 separated from the rest of said enclosed space 1707 by said piston 1703, when the actuator piston 1700 has been pressurized to the above mentioned 3½ Bar at a second a 2^nd longitudinal / 2^nd circular position 1705 until depressurized to e.g. ½ Bar when moving from said 1^st longitudinal / 1^st circular position 1706 - the actuator piston 1709 at said 1^st longitudinal / 1^st circular position has now a much bigger diameter that said piston at said 2^nd longitudinal / 2^nd circular position 1705. In order to deflate said actuator piston 1705 to atmospheric pressure - position 1713, where in case of a crankshaft the return takes place toward a 2^nd longitudinal position - the ½ Bar overpressure is being released in said enclosed space 1707 by retracting said piston 1703 away from the actuator piston 1709: movement 1710. Said actuator piston 1711 is increasing in diameter to its production size, which is slightly smaller than the diameter of said actuator piston 1700, which had been pressurized to 3½ Bar at said 2^nd longitudinal positoion 1705, within the wall of the chamber (not shown in this figure). Said piston 1703 is being retracted further away - movement 1712 - from said actuator piston 1711, so that a pump stroke 1716 toward said 2^nd longitudinal position 1714 can take place, pressurizing said actuator piston to 3 ½ Bar, when, in case of a crankshaft, the actuator piston has returned toward (171 ) a first longitudinal position.

Fig. 14B shows schematically the process of Fig. 14A in time, and this process is shown in a sub-chamber 1720 positioned around a circleround centre axis 1721, which has been stretched out as a straight line, which is additionally the time line. Said sub-chamber 1720 is normally moving in the direction of the arrow 1740, while said actuator piston 1722 is non-moving. However, in this drawing is the sub-chamber non-moving while the piston 1720 is moving. The piston 1722 is positioned at a 2^nd longitudinal / circular position and the fluid 1723 inside said actuator piston has been pressurized to e.g. 3½ Bar. The pump 1724 is comprising a piston 1725, a piston rod 1726, a chamber 1727 and a cam wheel 1728. Said cam wheel 1728 is resting on a cam surface 1729. Said piston 1725 is positioned at a 2^nd longitudinal piston (1730) of said pump 1724. The position of said piston 1725 remains unchanged when the actuator piston 1722 is moving from a 2^nd longitudinal / circular position to a 1^st longitudinal / circular position in said sub-chamber 1720, where the fluid 1723 is reducing its pressure to ½ Bar - actuator piston 1732. The cam wheel surface 1728 remains at its position, as the cam surface 1729 remains its height. Retracting the piston 1725 from position (1730) to position (1731) gives the actuator piston 1733 an internal pressure of 0 Bar (overpressure), and reduces its diameter to its production size. This is a result of the cam surface 1729 being sloped cam surface 1734 with a angle a in relation to the cam surface 1729, so that the cam wheel 1728 is becoming further away from said actuator piston 1733: cam wheel 1738. Directly thereafter returns the translation of cam wheel 1738 at end point 1735, and returns to said actuator piston 1733, which has been turning further to actuator piston 1736. When the cam wheel 1738 has come back to the original surface 1729, over the sloped cam surface 1739, which has an angle β (>90°) with said cam surface 1729. The actuator piston 1737 belongs to said position of said cam wheel 1728. It has to be emphasized that the reduction of size of the diameter of the actuator piston may be done gradually during a very small period of time, so that the actuator piston remains a contact with the wall 1748 of said chamber 1720.

Fig. 14C shows the configuration of Fig. 14B which enables an injection of fluid into the actuator piston, when it is at a 2^nd circular position. The cam wheel 1740 is now turning over a hose 1741, of which the chamber 1744 is comprising a wall 1742, and a fluid or a mixture of fluids 1743. Said hose 1741 has an exit 1745 to the enclosed space 1746 of the actuator piston 1747 which temporary closed, and only opened to said enclosed space 1746 of said actuator piston 1747, when the actuator piston 1747 is at a 2^nd position (Fig. 14B ref. nr. 1737) where it may be repressurized from the fluid in the hose 1741.

The description of Fig. 14D1 is showing classic (straight cylinder) pumps, which are communicating with the enclosed space of said actuator pistons, running in the same circular chamber. The chamber 1749, with a centre axis 1750 in a wheel 1751 - which is turning anticlockwise around an axle 1752, which is mounted with roll bearings 1753. Said chamber is comprising 4 identical sub-chambers 1754, 1755, 1756 and 1757. Said channel 1750 is comprising 5 fixed identical pistons 1758, 1759, 1760, 1761 and 1762, each at a different circular position to each other, thus having different diameters and internal pressures. Each piston has a pump part 1763, 1764, 1765, 1766 and 1767, which is fixed in the centre of each of said pistons 1758, 1759, 1760, 1761 and 1762. Each of said pumps has a piston rod 1768, 1769, 1770, 1771 and 1772, which is comprising a cam wheel 1773, 1774, 1775, 1776 and 1777, running over a cam shaft 1778. This cam shaft 1778 is comprising 4x identical lowered portions 1779, 1780, 1781, and 1782, there where a piston 1758, 1759, 1760, 1761 and 1762 need to be repressurized, and just before a piston need to be pressurized again. The actuator piston 1761 shows the use of the lowered portion for said pump to dashed 1761 '. The arrow 1783 shows the direction wherein said chamber 1749 is turning around said axle 1752. Fig. 14D2 is identical with Fig. 14D1, with the exception that the pump parts (comprising straight cylinders) 1763, 1764, 1765, 1766 and 1767 have been exchanged by pumps parts (comprising elongate conical cylinders) 1786, 1787, 1788, 1789 and 1789. The 2^nd longitudinal position of said pumps parts 1786, 1787, 1788, 1789 and 1790 are positioned closest to the actuator pistons 1791, 1792, 1793, 1794 and 1795.

Fig. 14E shows the section A-A of the motor according to Fig. 14D2 of this invention, comprising a circular chamber, mounted directly on a wheel of a vehicle. A section of a rim 1900, with a centre axis 1901, and its suspension on a brake disk 1902, having a centre axis 1903 and a brake pad 1904, which is mounted by bolts 1955 on a chamber housing 1905, in which a circular chamber 1906 is present, having a centre axis 1907, said chamber 1906 is shown in a section where a sphere type piston 1908 is in a first circular position according to the configuration of Fig. 14D2. The inside of said piston 1908 is communicating with an enclosed space 1909, which is mounted in a housing 1910, which itself is mounted by bolts 1922 on a part 1911 of a vehicle frame 1912 (not shown). The size of said enclosed space 1909 is regulated by a pump 1 13 with a conical chamber 1914, of which end of its conical chamber 1914 end is running by rollers 1915 over a cam profile 1916. Said cam profile 1916 is driven by an auxilliarly electric motor 1917 which is turning said cam 1916, and turning independently of said motor (comprising said circular chamber 1906 and said sphere piston 1908) by roller bearings 1924 around said main motor axle 1918. Shown are roller bearings 1919 for the chamber 1906 suspension on said main motor axle 1918, and a ball bearing 1920 for the cam profile 1916 on said main motor axle 1918. The main motor axle 1918 is mounted by bolts 1923 on said vehicle frame 1912 (not shown) as well. A pressure controller 1925 according to the configuration of Fig. 16 ("drive by wire"), which is communicating with a remotely positioned speeder 1927 (not shown). The pump 1928 of said pressure controller 1925 is communicating with a channel 1926 which is comprising the enclosed space 1909 of said actuator piston 1908. The electric motor 1917 is shown scematically as e.g. rotor 1928 which is fastened on the outside motor wall 1929, which is comprising said cam 1926. The anker 1930 is fastened in said main motor axle 1918, such that said anker 1930 is within said rotor 1928. The chamber housing 1905 is fastened to the main motor axle 1918 by nut 1931, and washer 1932. The extended axle end 1933 of said roller 1915 of said pump 1913 is guided in a groove, which is parallel with the centre axis 1934 of said pump 1913, such that a translating movement of the chamber 1914 of said pump 1913 is generated.

Fig. 14F is showing a scaled up detail of said circular chamber 1916 the section shown in Fig.l4E, when at a 1^st circular position, with a centre axis 1907 and chamber housing 1905, bolted together by bolt 1955. The sphere piston 1908 is shown in section. The wall 1939 of said sphere piston 1908 is comprising a reinforcement (not shown) according to Figs. 208E,F or Figs. 209A-C, and is at the end 1940, positioned opposite to the end 1941 closest to said pump 1913, mounted (e.g. vulcanized) on a closed end 1943 of a piston rod 1942. Said piston rod 1942 has a channel 1944, which is communicating through hole 1945 with the cavity 1946 of said sphere piston 1908. At the other end 1941 of the wall 1939 of said sphere piston 1908, is said channel 1944 communicating with the conical chamber 1914 of said pump 1913, and with said channel 1926 of the pressure controller (1925) (not shown). Said end 1941 is comprising a movable cab 1947, which is sealed on said piston rod 1942 by an O-ring 1948. The sphere piston 1908 is mounted (e.g. vulcanized) on said movable cab 1947, and this movable cab 1047 can slide over said piston rod 1942. For making it easier this drawing to comprehend, the wall 1941 of the piston 1908 is not drawn through the section wherein the contact between the wall 1941 of said piston 1908 and the wall 1948 of said circular chamber 1916 is taking place. The centre axis 1949 of the channel 1944 of said piston rod 1942. The centre axis 1934 of the chamber 1914 of said pump 1913. Said piston rod 1942 can translate within the cylinder 1950, and is sealed by two O-rings 1951 and 1952, respectively. The distance aa between the centre axis 1953 of said hole 1945 and said centre axis 1907 of said circular chamber 1916. The distance cc between the end 1954 of the movable cab 1947 and said centre axis 1907.

When a vehicle is comprising more than one wheel, it may be necessary to synchronize the motion of each wheel with the motion of each other wheel, if said wheels are rolling over the same surface. This may preferably be done by a computer, which is co-ordinating the pressure in each actuator piston in each sub-chamber per wheel, with that of each other wheel. This is shown by reference

1960, which is communicating with a computer (not shown) (1961).

Fig. 14G shows the same as Fig. 14H, with the exception that said actuator piston 1908 is shown in a 2^nd circular postition of said chamber 1916. Said movable cab 1947 has been sliding over said piston rod 1942 towards said closed end 1940, while additionally said piston rod 1942 has been sliding in said cylinder 1950, towards the pressure controller (not shown) (1925). Said hole 1945 is now positioned between said closed end 1940 and said movable cab 1947. Said distance aa (Fig. 14F) has been reduced to distance bb, while said distance cc (Fig. 14F) has been reduced to distance dd. Said slidings make it possible to adapt the position of said actuator piston 1908 to be in the center of the cross-section of said chamber 1916, at all circular positions of said actuator piston 1 08.

Fig. 14H shows the configuration of Fig. 14E, wherein between the rim 1900 of the wheel and the brake plate 1902, and said circular chamber housing 1916 has been built-on gearbox 1956, e.g. of the type of a planet gear.

Besides the computerized controlling of the pressure of each actuator piston, as described in Fig, 14E, it may be necessary to synchronize the change of gear of said gearboxes 1956, for each one wheel. This may preferrably done again by a computer, e.g. the computer 1961, which is already controlling the pressure in each actuator piston (Fig. 14E).

DESCRIPTION OF PREFERRED EMBODIMENTS updated from 19622

Fig. 141 shows that part of a pressure management system of a motor 1970, and 1971, resp. each mounted on at least two parallel positioned wheels 1972 and 1973, resp. of e.g. a car. The back wheels 1974 and 1975, resp. Said car is turning in a left corner, around a circle centre 1976. The left wheel 1972 closest to said center 1976 is turning with a smaller radius 1977, than the right wheel 1973, which has a radius 1978. The left wheel 1972 is turning with an angle 'a' and the right wheel with an angle 'b', where 'a' > 'b'. Consequently needs the left wheel turn slower than the right wheel, and these signals 1981 andl982 have to be send to the relevant motors 1972 and 1973. This is done by a sensor 1979 and 1980, sensing said different angles 'a' and 'b'. These signals 1981 and 1982, resp. are being transferred to a computer 1983, and being worked with, resulting in control signals 1984 and 1985, resp., so that said motors 1970 and 1971, resp. are changing each their speed accordingly.

Figs. 15A-E show several auxiliary power sources working together with the motor. The shown electric power lines have been carefully chosen.

Fig. 15A shows a H₂-fuel cell which delivers electricity to a motor, which is driving an ESVT-pump. Today (February 2011) is this solution very costly, but just on the website of the Carbon Trust was a message, that there was a technical breakthrough, which made it possible to use in the future a H₂-fuel cell in a car motor. The other difficulty is that the storage of H₂ is difficult and energy unfriendly.

Fig. 15B shows a solution which is a solution for the H₂ storage problem, because H₂ is stored as H₂0, and is coming free through electrolyses. Because the feasibility study showed that less than 10% of the current energy is necessary for driving, e.g. a car, in this way of generating and using H₂ in a combustion motor, which may result in rotation. An alternator is generating electricity, which is driving an electric motor for driving an ESVT-pump. The problem here is that the last mentioned process has an efficiency of only 25%.

The 0₂ which comes free at the electrolyses of conductive H₂0, may be used in the combustion motor, so that the burning of H₂ is still more efficient (turbo-effect). The H₂0 which comes free from the burning process in the combustion motor, may be re-used for deriving H₂ by electrolyses.

Fig. 15C shows a solution where the ESVT pump is directly driven by the axle of said combustion motor through a crankshaft, which now may be much smaller because the process of powering said pump is 100% efficient.

Fig. 15D shows a comparable solution as Fig. 15C, where the crankshaft has been exchanged by a rotational ESVT-pump, which makes the process still more efficient. The ¾ comes here from both electrolyses and from the solar voltaic cells.

Fig. 15E shows a solution where a big capacitor is used as the power source for the

ESVT-pumps. The big advantage is that this capacitor can be charged in a few minutes, and a car may drive say 500 km, when the capacitor has the size of a suitcase.

Fig. 15A shows schematically a storage tank 1630 for 0₂ (1631), which may be pressurized, and which has been filled up through channel 1632, which is connecting said storage tank 1630 with the outside (1633) of said motor. Said storage tank 1630 is communicating through a channel [1634] to a H₂-fuel cell 1606. Another storage tank 1600 for H₂ (1601), which may be cooled and may be pressurized, using electricity through an electric communication [1602], and which has been filled up through a channel 1603, which is connecting said storage tank 1600 with the outside (1604) of said motor. Said storage tank 1600 is communicating through a channel [1605] to a H₂-fuel cell 1606 wherein H₂ and 0₂ are being transformed into electricity, which is charging through electric communication [1607] either start battery 832B (short term, high current), or service battery 832C (longduring, medium current). Said channel [1605] is comprising a non- return valve 1608 (not shown). The potential difference required for operating the fuel cell 1606 is established by said electrical communication [1602]. The start battery 832B is electrical communicating [1609] with the starter 830 of the motor, while the service battery 832C is electrically communicating [1610] with a pump 820/826 of said motor. The motor, of which selected elements are rehearsed here, is treated in depth in Figures 11 A,B,G,H,I,J,K,L,M,N and Figure 12 A and Figures 13 A & B. Said motor is further comprising a pressure vessel 814/890, which is communicating with pump 826 and with piston actuator arrangement 800. The main axle 852 of said motor is communicating with alternator 850, which is charging through an electrically communication [1611] the service battery 832A (longduring, medium current). Said battery is electrically communicating [1602] with the cooling of tank 1600. The batteries 832A-C (incl.) are referred as one piece in other drawings of this patent application, with reference number 832, and have been charged ab works. The photo voltaic solar cell 833, which is additionally charging battery 832. The pressure storage vessel 814/890, which is being charged by a pump 820/826. The piston actuator module 800 of the motor, alternatively reduction valve system 1057 and 1058, as explained earlier e.g. Fig 11G, drive the main axle of the motor 852.

Fig. 15B shows schematically a tank 1612 for (conductive) H₂0 (1613), which has been filled up through a channel [1614], which is connecting said tank 1612 with the outside (1629) of said motor. Said tank 1612 is communicating through a channel [1615] to a vessel 1616 in which electrolyses 1617 of said water (1 13) is taking place. The exit [1622] of said vessel 1616 is communicating with a combustion motor 1620, which is communicating with its main axle 1621. Said channel [1622] is comprising a non-return valve 1618 (not shown). Said motor 1620 is burning the H₂ generated in vessel 1616 , so that motion occurs - here, rotation of said axle 1621. Said axle 1621 is communicating with an electric start motor 1623, and with an alternator 1624. Said alternator 1624 is charging by electric communication line [1619] battery 832B (for high current, short time) for said start motor 1623, or battery 832C (medium current, longduring). The battery 832A (medium-high current, longduring) is being charged by an altemator 850 through electric communication [1611], which is communicating with the main axle 852 of the motor. Said battery 832A is giving power through electric communication [1626] for the electrolyses 1617 in vessel 1616. The battery 832C is giving power through electric communication [1627] to pump 820/826 of the motor, while the battery 832B gives power to the start motor 1623 and 830, respectively through electric communication [1628]. Said batteries (832) have been charged ab works. The photo voltaic solar cell 833, which is additionally charging battery 832. The pressure storage vessel 814/890, which is being charged by a pump 820/826.. The piston actuator module 800 of the motor.

Fig. 15C shows schematically the process according to Fig. 15JB, where additionally a piston pump 1625 of the repressurisation cascade, so either 820 or 826, is directly communicating with the main axle 1621 of said combustion motor 1620 through a crankshaft 1636 and piston rod 1637. The photo voltaic solar cell 833 which is charging the battery 832, besides the alternator 850, which is communicating with the main axle 852. The battery 832 is electrically connected to the motor 1623 through an electric communication [1628]. The exit of the pump 1625 of motor function 820/826 is communicating by channel [828] with the motor, and particularly the pressure storage vessel 814/890, according to Figs. 11A,B„G or Figs. 12A, 13A,B. In this figure the electric output [1628] by the battery 832 provides electric communication to other functions of the motor, presented in previous figures.

Fig. 15D shows schematically in principle a comparable process of that of Fig. 15C, where the piston pump 1625 has been exchanged by a rotational pump 1635, which is communicating with said motor 1620 by axle 1621. Said rotational pump 1635 is communicating with pressure storage vessel 814 of Fig. 13B by channel [828]. The start motor 1623 is communicating with axle 1621 and gets its power from battery 832 through wires [1628] The battery 832 is being charged by photo solar cells 833' and alternator 850 through wires [1611], and is communicating with axle 1621. The battery 832 is connected to the motor functions 800 by wires [1627]. The photo solar cells 833' are providing directly ¾ to the motor 1620 by channel [1640]. This system may preferably be used together with the configurations shown in Figs.l3F,14B,C,D. The motor type according to Fig. 14D may be a specifically preferred embodiment. In this figure the electric output [1628] by the battery 832 provides electric communication to other functions of the motor, presented in previous figures.

Fig. 15E shows schematically a capacitator 1641 for instant storage of electricity 1642, which has been filled up through an electric wire [1643], which is connecting said capacitor 1641 with the outside (1644) of said motor. Said capacitor 1641 is communicating through a channel [1645] to other functions of the motor in Figs. 11A,B,C,F,G and Fig.l2A and Figs. 13A,B according to function 851 in said drawings. Said functions are comprising an axle 852, 866 and 1621, respectively, which are communicating with an alternator 850 or 1624. Said battery 832 is electrically connected by wires [1611] with said alternator 850 (not shown in Fig. 15E). The battery 832 is additionally charged by a photo voltaic solar cell 833. Additionally is said capacitor 1630 connected to said battery 832 by wires [1646] for charging purposes.

Fig. 16A shows a scaled up 2-way actuator of the Figs. 11G-R. The 2- way actuator is comprising two channels 3300 and 3301, which are communicating from the outside to the inside of the cylinder 3302, each communicating with a regulator (reduction valve) 3303, 3304, respectively which are controlled through valve means 3305 by a speeder 3306 - both regulators 3303 and 3304 are communicating to each other, so that one speeder 3306 can control both regulators 3303 and 3304.. There are two overflow channels 3307 and 3308, which communicate to each of the two spaces 3309 and 3310 on each side of the internal piston.3311. The O-rings 3312 and 3313, between said piston 331 1 and the wall 3314 of said actuator.

Fig. 16B shows a pre-study of the 2-way actuator of Fig. 16 A. It is concluded that a more quickly reacting system is that the piston is comprising the overflow channels. Additionally it is concluded that the regulators need to have each a stop function for its flow. And, that the overflow channels need to have each (1) an automatic contra valve function (e.g. according to Fig. 210E) and (2) a check valve.

ESTV - ASYNCHRONE CRANKSHAFT DESIGN - COMBINED USE OF COMPONENTS

Fig. 17A shows a complete cycle of an actuator piston in a conical chamber, using the ESVT. This is identical with Fig. lOA-C. Even though only the ellipsoide-ellipsoide/sphere type piston is shown, any type of inflatable actuator piston may be used.

Figs. 17B-H show a multiple cylinder motor, which is based on the 2-cylinder configuration of Fig. 17B. Fig. 17B is based on the one cylinder configuration of Fig. 17 A, where said configuration has been used twice, in such a way that simultaneously the power stroke of one chamber and the return stroke (which is not powered) of the other chamber are being performed.

Because the power stroke of an actuator piston is only performed from a 2^nd to a 1^st longitudinal position, said two chambers are pointing in opposite directions. The consequence is that the crankshaft configuration is such, that the connecting rods to these actuator pistons are positioned 180° in relation to each other ('asynchrone'). The result is that the motor delivers power at all times, and this configuration may be used in a stand alone 2 cylinder motor, or in a multiple (>2, and preferably even number) cylinder motor. A flywheel may be redundant, omission of which may reduce the weight of the vehicle.

Both actuator pistons may or may not be commumcating with each other through the enclosed spaces of said crankshaft (which may be comprising two connected sub-crankshafts, one for each actuator piston), each belonging to a different actuator piston. The communication between the enclosed spaces may be through the channels in the sub-crankshafts and/or through a channel outside said crankshaft.

said enclosed spaces may be separated, e.g. at the connection point of said sub- crankshafts (together comprising said crankshaft) by e.g. a tightening rod 1270 (Fig. 11X), which may be positioned between said enclosed spaces.

In this configuration of the actuator pistons may it very well be possible to combine said two ESVT pumps into one pump, as the pressure increase and decrease, respectively to each of the actuator pistons, is reversed, at the same point of time, while the total volume of the enclosed spaces may be remained. An ESVT-pump is e.g. directly communicating with one of the enclosed spaces, while said ESVT-pump is communicating indirectly through an external channel with the other enclosed space. There may be valves functioning in both flow directions, to and from each enclosed space per actuator piston (e.g. by the use of valve actuators according to Fig. 210E or Fig. 21 OF), which are opening and closing the connection between said ESVT-pump and said enclosed spaces. Said valves may be controlled by either the pressure of said ESVT-pump and/or by tappets, which may be communicating with a camshaft (which may be communicating with the main auxiliary power line, e.g. an auxiliary H₂ combustion motor) or may be communicating with a computer (not shown).

The change of pressure inside the actuator pistons is when said actuator pistons are in the l^st/2^nd longitudinal positions and in the 2^nd/l^st longitudinal positions, respectively. When the camshaft may be regulating the opening and closing of the actuator piston + check valve assemblies, than said camshaft may have twice the speed of the axle, where the crankshaft of the ESVT-pump is communicating with.

The piston-chamber combinations for each of the enclosed spaces in a sub-crankshaft, which are changing the speed/pressure in a cylinder, may only be used for one cylinder. These piston-chamber combinations are communicating with each other through the electric pressure regulator of the 2-way actuators, which is moving the piston rod of each of said piston-chamber combinations, and is thus communicating with the external speeder. However, it may be possible that one of the two piston-chamber combinations may be deleted, and exchanged by the same configuration which has been used to cut one of the ESVT-pumps, whereby the settings of the piston-chamber combination is synchronous. The many valves may be making the configuration vulnerable for n isfunction.

Instead of toothed belts at the power side of the auxiliary motor, there where the pump(s) are being driven, may very well be exchanged by gear wheels.

When said second and third enclosed spaces may be communicating with each other, e.g. at the connection point of said sub-crankshafts (Fig. 11W, W), e.g. through a movable piston (Fig. 171), which may be mounted in the channel which is comprising said enclosed spaces. Said piston is a double functioning type, so that when it is moving, e.g. towards said second enclosed space, thereby increasing the pressure in said second enclosed space of one of the actuator pistons, it simultaneously is decreasing the pressure in said third enclosed space of the other actuator piston. Said double working piston is actually the ESVT-pump of that configuration of the motor. It is additionally possible that said double working piston is positioned outside said crankshaft. A motor, further comprising two cylinders, wherein the 2 longitudinal position of one cylinder is at the same geometrical level of the 1st longitudinal position of a second cylinder, both actuator pistons are communicating with each other through a crankshaft, said crankshaft is comprising two connected sub-crankshafts, one for each actuator piston, where the connection rods to these actuator pistons are positioned 180° from each other.

A motor, further comprising ESVT pumps for each of the- cylinders, wherein said pumps are combined for said two cylinders into one pump, through communication of the enclosed space of one of the actuator pistons with the enclosed space of the other of the actuator pistons, said enclosed spaces being comprised in said crankshaft, said enclosed spaces are communicating with each other at the connection point of said sub-crankshafts.

A motor, further comprising valves, which are opening and closing the connection between said ESVT-pump and said second or third enclosed spaces, while each connection has a check valve or check valve function, said valves are controlled by either the pressure of said ESVT-pump and/or by tappets, said tappets are communicating with a camshaft, which is communicating with the main axle of an auxilliarly motor.

A motor, further comprising more than two cylinders, where each added cylinder is communicating through the enclosed spaces of the connected sub-crankshafts of the existing sub-crankshafts.

In Fig. 171 is a 2-cylinder motor been disclosed, where the enclosed spaces of each chamber in each sub-crankshaft have been separated by a straight channel in which a two-way piston is moving, and which is communicating with each enclosed space.

In Fig 17A the ellipsoide/ellipsoide-sphere actuator piston 217 is shown at the first longitudinal position. Said actuator piston is inflatable and runs in a chamber with different cross-sectional areas at the first and second longitudinal positions. The cross-sectional area and circumferential length at the second longitudinal position are smaller than the cross-sectional area and circumferential length at the first longitudinal position. Arriving at the first longitudinal position, the actuator piston is at the final position of the power stroke. During the power stroke the actuator piston moves from the second longitudinal position to the first longitudinal position under influence of the pressurised fluid inside the piston container.

The enclosed space with which the fluid in the piston container is in constant and open communication remains equal during the power stroke. The enclosed space of the piston actuator is communicating with a channel in which a valve is controlling the volume of the enclosed space. At the time of the power stroke the valve is located closest to the actuator piston.

During the movement from the second longitudinal position to the first longitudinal position a pressurised ellipsoide shaped piston 217' has expanded into sphere shaped piston 217, and with the expansion of the piston container the pressure inside said piston gradually lowers. At the first longitudinal position the fluid inside said piston is still on a small overpressure to assure a good sealing to the chamber walls. The shape of piston 217 may also be ellipsoide.

Where the position of the valve remains unchanged during the power stroke, the valve is retracted further away from the actuator piston. Such that the volume of the enclosed space increases and the internal pressure drops to the pressure of when the piston was produced. The fluid in the enclosed space and the piston container are in constant and open communication with each other. Hence when there is a pressure difference between the fluid in the piston container and the enclosed space a new equilibrium will be established.

In Fig 17A the valve moves from level "0" to "1" . The depressurised production shaped piston 217", located at the first longitudinal position, is ready for the return stroke. During the return stroke the actuator piston assembly is relocated to the second longitudinal position and the volume of the enclosed space remains equal, the valve setting "1" is maintained. When moving from the first longitudinal position to the second longitudinal position the piston is depressurised and might be free from the wall or just engaging it, but not seal the upper volume in the chamber from the volume underneath the piston. The returned piston 217"' is now held by the wall of the conical chamber and keeps its shape when pressurised to piston 217'. Pressurisation is realised by changing the valve's position in the channel the enclosed space is communicating with. The valve is extended from level "1" to "0", by decreasing the volume of the enclosed space the pressure is increased. The pressurised piston will move from from the second longitudinal position to the first longitudinal position again, completing one entire cycle. The piston expands, decreasing the internal pressure, to the initial piston shape 217. The movement is driven by the force on the wall of the chamber due to overpressure in the piston and the reaction force provided in response on the actuator piston. As the main axle, where the actuator piston is connected/attached to, receives energy from the mechanical movement it is called the power stroke. Next to a valve in the channel, various configurations can manage the pressurisations and depressurisation of the actuator piston. In Fig 17B a 2-cylinder configuration is presented. Both cylinders are identical to Fig 17A, only the internal orientation is 180° different. Such that when, for instance, the actuator piston in cylinder assembly A is at the start of the power stroke the actuator piston of cylinder assembly B is at the start of the return stroke. In Fig 17B this is represented by rotating the cylinder configuration by 180 degrees, but in the motor there are multiple possibilities to realise this e.g. by placing the cylinders parallel and rotate the crankshaft connection for cylinder B over 180° with respect to the one of cylinder assembly A. The cylinder pressure systems may be communicating with each other or have their own support systems. The main crankshaft of the motor comprises two sub-crankshafts, one for each cylinder-piston assembly. The cycle of the actuator piston in the conical chamber has been explained in the description of Fig 17A and the installation of the cylinders and the processes in the motor are treated in Fig 17C-H.

In Figures 17C - 17H a process description is given of one complete cycle of a motor configuration consisting of two cylinders. The configuration of the 2-cylinder motor disclosed consists of one main axle comprising two sub-crankshafts, where the enclosed spaces of each chamber in each sub-crankshaft have been seperated by a tightening rod 1270. The cylinders run a-synchrone (180 degrees difference), so when one cylinder starts the power stroke the other cylinder is at the start of the return stroke, like was presented in Fig 17B.

In the motor one ESVT pump is replaced by an inflow/ouflow connector, which is connected to the remaining ESVT pump. By means of valves 459/423 and 462/422 the flow to pressurise and depressurise both pistons is controlled. For each cylinder a set of valves is installed according to the concept of Figs 210E and 21 OF, hence one for the inflow and one for the outflow of the fluid. The valves are controlled by pressure and tappets in communication with the cams on a camshaft.

Both the crankshaft of the ESVT pump and camshaft are driven by an H₂ combustion engine via gear wheels and toothed wheel-belt configurations, enabling various speed (pre)settings. In Figs 17 C-H the rotational speeds of the camshaft, pump-crankshaft, and main axle are the same.

The remaining ESVT pump is of a special type where the volume atop the piston is connected to one cylinder assembly and the volume underneath the piston is connected to the other cylinder assembly. Because the cylinders run asynchronous, this arrangement provides the desired pressurisation scheme; low pressure at one side of the ESVT pump piston for the piston actuator which needs to depressurise and high pressure for the piston actuator that needs to be pressurised. The ESVT pump 8000 with special

configuration can be used for more motor configurations, and is for example applicable in Figs 17C-17H. For each set of valves there is a cam installled on the camshaft. Each cam provides two different signals during one rotation, once for the inflow valve and the other time for the outflow valve. The cams of each valve set are installed identically on the camshaft, so that when the first signals is provided by the first cam, the second cam also gives the first signal, and half a rotation further both cams give the second signal. Because the cylinders run asynchrone: when the first signal from the first cam is used for the inflow valve, the first signal from the second cam is used for the outflow valve of the other cylinder assembly, and vice versa for the second signal. A different configuration of the cams is possible as well, as long as it leads to the desired functioning of the valves.

The valves are of a special type, as described in Fig 211 Only when the valve piston is closed and there is an over-pressure in the direction of the valve actuator a flow is possible. The over-pressure is with respect to the outflow chamber of the valve plus the preset strength by the spring force supporting the piston core. The channel within the valve is in communication with the inflow chamber of the valve. By equal pressure in the inflow chamber and valve channel the valve actuator is kept in place, hence closed position. When the valve piston receives a signal by the appropriate cam and closes, the communication between the valve channel and inflow chamber is cut off. When in this setting an over-pressure occurs, the valve opens. At the moment the valve piston closes it does not only block the communication line of the valve channel with the inflow chamber, but also opens a channel for communication from the valve channel to the outflow chamber. Such that the pressure in the valve channel switches upon closure of the valve piston from the inflow chamber's pressure to the outflow chamber's pressure. The pressure in the valve channel does not need to be overcome as it is in equilibrium with the outflow chamber. Upon removal of the signal from the valve piston by the cam the valve actuator returns to its closed position, the communication by the valve channel to the inflow chamber is re-established and the communication to the outflow chamber is cut off.

For the inflow valve of the valve set, controlling the pressurisation of the actuator, the ESVT pump is the inflow chamber side and the piston actuator with accompanying enclosed space the outflow chamber side. For the outflow valve it is the other way around. The valve piston is closed by the cam signal, which is once per rotation of the camshaft. When during such closure of the valve piston the pressure difference over the valve is positive a flow of fluid into or from the cylinder is possible. Furthermore the motor is based on the configuration of Fig 11R and the auxilliarly power source, a ¾ combustion engine, is according to Fig 15D.

For Fig 17C the cylinder 800L is at the second longitudinal position and cylinder 800R at the first longitudinal position. The ESVT pump decreases the volume atop in the cylinder and pressurises the fluid in the channels of cylinder assembly comprising 800L. By decreasing the volume atop, the ESVT pump

29 increases the volume underneath and hence lowers the pressure in the 800R cylinder system. The camshaft is providing a signal to the inflow valve of the channel in communication with cylinder 800L. The valve piston closes, the pressure in the channel of the valve is brought in equilibrium with the pressure in the enclosed space associated with actuator piston of 800L. The pressure from the ESVT pump builds up and is larger as the pressure in the enclosed space in direct and open communication with cylinder 800L. By the overpressure the valve actuator pushes the core pin aside and the fluid can flow in the direction of the cylinder 800L, pressurising the piston and preparing it for the power stroke. The outflow valve of 800L does not receive a signal, hence the valve piston is open and no flow is possible.

The camshaft has a second cam, which also gives the first signal, for cylinder assembly 800R. As the cylinders run asynchronous the communication of this first signal from the second cam is with the outflow ^"valve of 800R. The valve piston of the outflow valve of piston 800R closes and hence a flow from the actuator piston to the ESVT pump is possible. The inflow valve of 800R does not receive a signal, and hence no flow of fluid towards the actuator piston is possible. At the moment of Fig 17C the piston actuator of 800R is in the first longitudinal position, at the end of the power stroke and starting the return stroke. The piston container is still at a little over-pressure to assure good sealing and contact to the wall. The ESVT pump's lower end has increased its volume and hence decreased to low pressure. By closure of the valve piston the valve channel's communication switched from the actuator piston and associated enclosed space to the ESVT pump. The overall pressure situation is such that there is an overpressure over the valve actuator from the actuator pistonand associated enclosed spaces to the ESVT pump. A flow will initialise from the piston and enclosed space towards the ESVT pump, this flow will continue until the pressures at both sides of the valve are in equilibrium (neglecting the small force of the spring supporting the core pin), or when the valve piston opens again and interrupts the communication.

Fig. 17C left shows a scaled up left part of Fig.l7C.

Fig. 17C right shows a scaled up right part of Fig.l7C.

In Fig 17D the motor system axles have rotated one sixth of a rotation further. In Fig 17C the ESVT pump was decreasing the volume atop of the piston, and in Fig 17D the the piston is staying in a position where the volume atop is small and the volume underneath is large. By the rotation of the crankshaft the fluid above the piston is slightly more compressed, and underneath more expanded. The pressurisation by the ESVT pump could also be split in a top half with high pressure and a lower half with low pressure, by which the shift from one side to the other side is of importance to indicate the change with the earlier situation. This split in a top and lower half applies for the cylinder assembly 800L, and for cylinder assembly 800R the situation is opposite. Next to the crankshaft determining the volumes in the ESVT pump also the camshaft has rotated. In this new situation the cams provide no input signal to any of the valves. Consequently the valve pistons are open and no flow towards or from the actuator piston and enclosed spaces is possible. The pressurised

29 piston in cylinder assembly 800L is moving from the second longitudinal position towards the first longitudinal position by the resultant reaction force of the wall exerted upon the piston.During the upward movement the piston expands under influence of the piston internal pressure, maintaining a good sealing and contact to the chamber's wall. The piston of assembly 800R is depressurised and moving downward with no contact to the wall or just engaging the wall.

Fig. 17D le t shows a scaled up left part of Fig.lTD.

Fig. 17D right shows a scaled up right part of Fig.l7D. In Fig 17E the piston of cylinder assembly 800L arrives at the first longitudinal position, the end of the power stroke. The actuator piston of cylinder assembly 800R, still depressurised, arrives at the second longitudinal position, the end of the return stroke. The various shafts have rotated 60 degrees further. The piston of 800L has maximally expanded into the chamber and is still under a little over-pressure to assure a good sealing to the walls. The pressure inside the piston of 800L, and hence the pressure in the channel communicating with piston 800L is at its lowest value of the power stroke at the highest position in the chamber (or at the first longitudinal position). The camshaft is not providing a signal to the valves and hence the valve pistons are open and no inflow or outflow is possible. The ESVT pump driven by a connector to the crankshaft, is still oriented such that the volume atop the ESVT pump's piston is minimal and consequently resulting in a high pressure, and the volume underneath the piston remains large with a low pressure.

During the first half of the process in Figs 17C-17E the piston actuator of cylinder 800L has performed the power stroke, providing power to the main axle. The main axle rotates with the same speed as the crankshaft and camshaft. The piston actuator of 800R only translates, at the cost of minimal work, from the first to the second longitunal position. This required work is provided by the main axle. Other elements requiring energy are powered by the auxilliarly power source, for example the crankshaft and camshaft.

Fig. 17E left shows a scaled up left part of Fig.l7E.

Fig. 17E right shows a scaled up right part of Fig.l7E.

In Fig 17F the cams on the camshaft are providing a signal again. The camshaft has rotated further and rotated up to here over 180 degrees, relative to the starting situation in Fig 17C. Also the signal by the cam is the other one as the one effective in Fig 17C. The signal is closing the valve piston of the outflow valve of cylinder 800L. The pressure in the valve channel is equal to the little over-pressure in the piston actuator at

30 the end of the power stroke. With the closure of the valve piston the valve channel exchanges fluid with the ESVT pump to balance these two pressures. The ESVT pump piston has made a stroke to enlarge the volume atop of the piston and consequently decrease the pressure in this space. The little over-pressure of piston actuator 800L is having a positive pressure difference over the valve outflow chamber's pressure, being equal to that of the ESVT pump's top end. The positive pressure difference will move the valve actuator, pushing the core pin aside, and enable a flow of fluid from the actuator piston towards the ESVT pump. This depressurises the piston and prepares it for the return stroke, where it has to be free from the wall or just engaging it. As the valve piston of the inflow valve for 800L does not receive a signal by the cam it remains open, and does not allow a flow through the valve.

For the valve set controlling the pressurisation of the piston and associated enclosed spaces of 800R, the signal by the second cam closes the valve piston of the inflow valve. The outflow valve's valve piston remains open and hence does not facilitate a flow from the piston to the ESVT pump. With closing the valve piston of the inflow valve the valve channel's pressure is brought in communication with the internal volume of the depressurised piston, having just finished the return stroke to the second longitudinal position. As the ESVT pump had made a stroke and the volume underneath the ESVT pump's piston has decreased and the fluid in this volume is pressurised. The pressurised fluid in the ESVT pump with which the cylinder assembly 800R is in communication is resulting in a positive pressure difference over the valve actuator. This pressure difference enables a flow from the ESVT pump to the actuator piston and associated enclosed spaces. Bringing the piston container under pressure, which consequently wants to expand, but as the piston's outside is held by the walls of the conical chamber it instead exerts a force on the walls, which results in a reaction force on the piston. This reaction force has a component in the chamber's longitudinal direction and drives the piston. So by pressurising the piston of 800R it can perform the upcoming power stroke.

In Fig 17F the situation of cylinder assembly 800L and 800R is that of the other cylinder assembly half a cycle before in Fig 17C. The pressures, valve settings, longitudinal positions, etcetera, are comparable to what it was in Fig 17C for the other piston to have the motor operating smoothly.

Fig. 17F left shows a scaled up left part of Fig.l7F.

Fig. 17F right shows a scaled up right part of Fig.17F.

In Fig 17G and 17H the axles rotate each time a sixth rotation further, completing the cycle. The cams on the camshaft give no signal in these two steps. Consequently the valve pistons of the inflow and outflow valves of both valve sets remain open. As valve pistons are open the pressures pushing on the actuator valves, from each valve's inflow chamber, is counteracted by the valve channel's pressure, which is in constant

30 communication with the valve's inflow chamber. As the valve actuators remain in position no flow between the ESVT pump and piston actuators takes place.

Also the setting of the ESVT pump remains comparable to that of Fig 17F. The volume above the piston in the ESVT pump remains large resulting in a low pressure of the fluid atop, this volume is communicating with the cylinder assembly 800L. And the volume underneath the piston, in communication with the cylinder assembly 800R, is kept small, resulting in a high pressure. As there is no flow of fluid in Fig 17G,H it is of no further consequence, but for the transition again from Fig 17H to Fig 17C, it is the pressure change by the return stroke of the piston in the ESVT pump that is of importance to create the positive pressure differences for the appropriate valves.

In Fig 17G the piston assembly 800L is moving from the first longitudinal position to the second longitudinal position. The piston moves from the first longitudinal position to the second longitudinal position. The piston is in an unpressurised state and is free from the chamber's wall, or just engaging the walls. At the same time cylinder assembly 800R is performing the power stroke from the second longitudinal position to the first longitudinal position. Hereby the pressurised piston expands, lowering the internal pressure and maintaining a good contact to the conical chamber's wall.

In Fig 17H the piston actuator of assembly 800L finishes the return stroke and arrives in the small end of the conical chamber, here the cross-sectional area and circumferential length are smallest. The pressurised actuator piston of cylinder assembly 800R arrives at the first longitudinal position, where the piston has maximally expanded in the conical chamber's large end, where the large cross-sectional area and circumferential length are largest. There remains a little over-pressure in the piston to assure a good sealing to the walls up to the last movement of the power stroke. At this point the normal direction of the walls is perpendicular or almost perpendicular to the chamber's longitudinal axis. Fig. 17G left shows a scaled up left part of Fig.l7G.

Fig. 17G right shows a scaled up right part of Fig.l7G.

Fig. 17H left shows a scaled up left part of Fig.lTH.

Fig. 17H right shows a scaled up right part of Fig.l7H.

The next step in the ongoing operation of the motor is the same as Fig 17C again. Hence this cycle of six intermediate steps of Fig 17C-H describe the full cyclus of the motor comprising two cylinders operating asynchronous.

30 In Fig 171 an example is disclosed of how it could look when the ESVT pump is installed at the connection of the two sub-crankshafts. The motor elements are identical to the motor described in Fig 17C-17H. The ESVT pump may be operated by a mechanism inside the cylinder which is in line with the crankshaft's axis e.g. a worm wheel or an installation by springs. The piston inside the straight channel forming the ESVT pump may also be driven by an external system. The two-way piston is moving in the chamber and thereby enlarges the volume of the enclosed area it moves away from and decreases the volume of the enclosed space it moves towards. Respectively lowering and increasing the pressure in the enclosed spaces. The piston simultaneously seals both enclosed areas.

30 ESTV - SYNCHRONE CRANKSHAFT DESIGN - COMBINED USE OF COMPONENTS

Fig. 18A-G (incl.) show multiple cylinder motors, based on a two cylinder configuration, which is based on the 2-cylinder configuration of Fig. 18 A, which is based on the one cylinder configuration of Fig. 17A, which refers to Figs. ΙΟΑ,Β. However, any inflatable actuator piston type may be used.

In Fig. 18A are two cylinders shown, which have simultaneously combined in time the power stroke of each cylinder. Both actuator pistons are communicating with each other through a crankshaft (which may be comprising two sub- crankshafts), where the connection rods to these actuator pistons are positioned 0° from each other.

This is done by a configuration of two identical piston-chamber combinations, where the 2^nd longitudinal position of one cylinder is at the same geometrical level of the 2^nd longitudinal position of the second cylinder. The return stroke is thus not powered, and such a configuration may be combined with other configurations (motor comprising > 2 cylinders) in order to fill the power gap at the return stroke. Another solution may be the use of a flywheel.

The ESVT pumps may be combined to one pump for said two cylinders into one pump, through connecting the enclosed spaces of the actuator pistons, e.g. at the connection point of the sub-crankshafts.

If another group of actuator pistons is added to said motor, and the strokes of the added piston-chamber combinations are identical with those of said motor, than the configuration of Fig. 18 can be used for the total group - preferably one ESVT-pump may be used for the whole group of piston-chamber combinations, as well as one piston-chamber combination for the pressure/speed control.

If another group of actuator pistons is added to said motor, and the strokes of the added piston-chamber combinations are opposite to those of said motor, than the configuration of Fig. 17 can be used for the total group - one ESVT-pump may be used for the whole group of piston-chamber combinations in combination with an external channel, and non-return valves and valve actuators in both flow directions (please see Figs. 17C-17H (incl.). The two crankshafts of both groups of piston-chamber combinations may be communicating with each other, whereby the channel inside each crankshafts may preferably be separated, e.g. by a filler (e.g. a tightening rod 1270 of Fig. 11X). A power balance may arise in said motor, whereby the power srokes of the various actuator pistons are configured such that the motor provides a constant power. In Figs 18B - 18G the pressurisation scheme of the motor during one cycle is disclosed. The motor has a two cylinder configuration as shown in Fig 18A. The piston actuators of each cylinder assembly are continuously at the same stage in the cycle, the piston actuators run in parallel.

The motor is based on Fig 11R as well, as the motor of Fig 17C-17H was based on this concept, the major differentiation is in the piston pressurisation. The auxiUiarly power source is an H₂ combustion engine, which is forced liquid cooled. The auxilliarly power source provides work for the pumps, battery and crankshaft.

The two piston actuators installed on the crankshaft are connected to one ESVT pump. As the pressure scheme of both pistons is equal, the pressure settings required from the ESVT pumps by the pistons actuators are the same. This allows simple joining of the two ESVT pumps for each actuator piston independently into a single shared ESVT pumpl055, only the size hereof might possible be adapted. Next to the ESVT pump also one piston chamber combination 1050 is installed for the pressure/speed control in this 2 cylinder configuration. The communication between the two actuator pistons takes place at the connection of the two subcrankshafts, where the second and third enclosed spaces are connected as disclosed in Fig 11 or W.

No valves are installed between the ESVT pump and the enclosed spaces or piston actuators of assembly 800L and 800R. To interrupt the connection between the ESVT pumps and the actuator piston, the connector contains holes to enable a flow of fluid towards or from the ESVT pump, or block this communication and set the amount of fluid in the enclosed space and associated piston. An example of such a facilitating connection between the actuator piston assembly and a crankshaft with an enclosed space is given in Fig 1 IT.

In Fig 18B the communication line from the enclosed spaces in subcrankshafts to the associated piston actuator is open allowing a flow of fluid. The actuator pistons have just finished the return stroke and are at the second longitudinal position. The ESVT pump's crankshaft has made a stroke upward decreasing the volume inside the chamber and increasing the pressure of the fluid in the ESVT pump. With the communication line to the actuator pistons being open the pressurised fluid can flow into the depressurised actuator pistons. During the return stroke the actuator pressure are depressurised not to touch the walls or just engaging it, not to seal the volume in the chamber underneath the piston from the volume above. And with the pressure in the ESVT pump being larger as the pressure in the piston actuator, the high pressure fluid flows into the piston actuator. The pressurisation of the actuator pistons establishes a good contact to the chamber walls and the overpressure makes the piston actuator

30 prone to expand, which is obstructed by the chamber wall, but due to the conical shape the reaction force results in the upward movement of the piston actuator towards the first longitudinal position.

Fig. 18B left shows a scaled up left part of Fig.l8B.

Fig. 18B right shows a scaled up right part of Fig.l8B.

In Fig 18C the piston actuators are halfway the power stroke of the motor, the crankshaft of the motor is rotating upwards. The situation for both cylinder assemblies is equal, as the piston actuators move synchronous. The crankshaft of the motor has rotated a little further closing the communication line between piston actuator and the enclosed space in the subcrankshaft, which is in constant and open communication with the ESVT pump. By the over-pressure the pistons expand into the enlarged area of the conical chamber. The piston's internal pressure decreases as there is no communication with the ESVT pump and the internal volume has increased. The ESVT pump maintains the small volume in the chamber, keeping a high pressure in the connected systems.

Fig. 18C left shows a scaled up left part of Fig.l8C.

Fig. 18C right shows a scaled up right part of Fig.l8C.

In Fig 18D the piston actuators arrive at the end of the power stroke. The pistons have maximally expanded in the conical shaped chamber. The pistons have moved to the first longitudinal position in the chamber. Although the volume in the actuator piston has increased, the fluid inside the piston is on a little over-pressure to estabKsh a good contact to the chamber walls for the whole power stroke. The crankshaft of the motor where the pistons are connected to, comes at a semi-rotation with respect to starting situation in Fig 18B. The holes in the connector from the piston rod to the enclosed space in subcrankshaft are closed, consequently there is no communication between the piston actuator fluid and the ESVT pump, or other piston actuator, as the enclosed spaces of the subcrankshaft are connected at the . The amount of fluid in the piston remains the same. The fluid in the ESVT pump is at high pressure by the small volume in the chamber. Fig. 18D left shows a scaled up left part of Fig.l8D.

Fig. 18D right shows a scaled up right part of Fig.l8D.

30 In Fig 18E the crankshaft of the motor has turned a litde further, whereby the holes between the enclosed space in the crankshaft and the piston rod open and a flow of fluid is possible. The crankshaft of the ESVT pump has made a stroke such that the connected piston in the the ESVT pump is moved away from the pump chamber's outflow and the volume in the ESVT pump is enlarged and the pressure decreased. The decreased pressure in the ESVT pump is less as the little over-pressure in the piston, and consequently the fluid from the piston will flow out in the direction of the ESVT pump, depressurising the piston. By loosing the internal pressure the piston changes shape, from the sphere- ellipsoide shape in contact with the walls at the first longitudinal position, to an ellipsoide shape free of the wall or just engaging it. The piston may also be of a different configuration with an accompanying shape scheme that can differ from this one. The piston actuators of both cylinder assemblies 800L and 800R are at the start of the return stroke.

Fig. 18E left shows a scaled up left part of Fig.l8E.

Fig. 18E right shows a scaled.up right part of Fig.l8E.

In Fig 18F the actuator pistons 800L and 800R are in the middle of the return stroke. The crankshaft of the motor is moving downward, providing the work to move the depressurised cylinders from the first to the second longittidinal position. The actuator pistons remain depressurised as the communication in the connector is interrupted again. The amount of fluid in the piston systems remain equal, and as the volume remains the same the pressure is also constant. The piston stays in the shape it has at the end of the stage presented in Fig 18E. The volume of the chamber in the ESVT pump remains large such that upto closure of the communication to the piston the fluid in the piston flows in direction of the ESVT pump. Fig. 18F left shows a scaled up left part of Fig.18F.

Fig. 18F right shows a scaled up right part of Fig.l8F.

In Fig 18G the piston actuators complete the cycle and arrive at the second longitudinal position. The ESVT pump is slightly decreasing the volume in the chamber again, but the pressure stays low. Also the holes for communication between the ESVT pump and actuator piston are closed. During the power stroke the piston actuators perform work on the crankshaft to power connected systems, while during the return stroke of both piston actuators the crankshaft is providing work to move the piston actuators, consequently the power supply by the motor is not constant.

30 Fig. 18G left shows a scaled up left part of Fig.l8G. Fig. 18G right shows a scaled up right part of Fig.l8G.

CT - CRANKSHAFT DESIGN - COMBINED USE OF COMPONENTS

Fig. 19A shows a one cylinder motor, based on Figs. 11B, 11C, where some parts have been worked out further - the auxiliary power source is e.g. chosen as a combustion motor, which is burning H₂, derived from electrolyses of H₂0. The water reservoir 1612 can be filled with H₂0 1613 through filler opening 1614 by an external source. From said water reservoir H₂0 can be transported to vessel 1616 by channel [1615]. The power required to perform the electrolyses 1617 in said vessel is provided by communication line [1069] which is in contact with the battery 832. Battery 832 may be charged by solar voltaic cells 833 and receive energy by the alternator 850. Said alternator is in communication with the main crankshaft 852 of the motor by a toothed belt and gear wheels. The battery may be providing a signal to the electric starter motor 830. Another communication line [1064] from the battery may be giving input to the reduction valve 840, which controls the fluid flow from the pressure storage vessel 814 through channel 829 to the inflow connector of the second enclosed space of the piston cylinder assembly 800L. The setting of the check valve 840 is controlled by speeder 841. The output of the electrolyses process, H₂, is fed by channel [3545] to the combustion engine 3525. Optionally the 0₂ is transported, by a separate channel [3546], to the combustion engine 3525. In said engine, under control of a signal by communication line [1069], the H₂ and 0₂ are processed at the creation of water, which may be fed in return (not shown) to said water reservoir 1612. The combustion engine can also generate heat which may be conducted away by a heat exchanger and used for a secondary application outside this motor. The combustion engine powers a shaft to. which piston pump 826 is connected. Said piston pump pressurises the fluid that comes by channel [825] from the outflow connector on the crankshaft, connected to the third enclosed space of the cylinder assembly. The free end of crankshaft 852 can be connected a flywheel 835, clutch 836, or gearwheel 837 (not shown).

The piston assembly 800L operates according to the consumption technology as described in Fig 11 A. The fluid in the second enclosed space in the crankshaft is at the pressure of the pressure storage vessel 814 or a reduced pressure after passing by reduction valve 840, while channel [825] connected to the outflow connector is at a low pressure, although the pressure can differ by the one way direction valve at the end of said channel controlling a positive pressure difference with respect to the pressure of piston pump 826. The piston actuator is connected to the crankshaft with a connector described in Fig 1 ID. The second and third enclosed space are not in communication with one another, as the channel is interrupted in the connector. Said connector allows a flow of the fluid from the second enclosed space with the piston actuator at the second longitudinal position. And between the third enclosed and the piston actuator when the piston assembly is in the first enclosed position. At said first longitudinal position the little over-pressure, still present in the actuator piston, establishes a flow of fluid into the third enclosed space due to the lower pressure in channel [825]. The piston becomes depressurised and free from the chamber's wall or just engaging it, not to seal the volume above the piston from the volume underneath. During the return stroke, by the rotation of crankshaft 852, the communication between the second and third enclosed space with the piston actuator is closed. And when the piston arrives at the second enclosed space the communication with the second enclosed space is open. Said actuator piston is depressurised and the second enclosed space is at the pressure by said pressure storage vessel and said reduction valve, consequently the flow of fluid will be in the direction of the actuator piston. The pressurised piston expands in the chamber and by the force on the wall receives a reaction force in return. This force drives the actuator piston upward to the first longitudinal position. Said expansion of the piston and movement to the first longitudinal position is the power stroke.

Fig. 19B shows a two cylinder motor, based on Fig. 19A with Consumption Technology, where the two cylinders have been positioned mirrored to the center line of the connection of the sub- crankshafts. The 3^rd enclosed spaces (exits) of the two piston actuators 800L and 800R are communicating with each other through the connection of the two sub-crankshafts, while the 2^nd enclosed spaces (inlets) are commumcating externally with each other (with a check valve), and where the crankshaft (comprising of two sub-crankshafts) is designed, so that the power strokes of each actuator piston are moving in the same (0°) direction (synchronous), according to the principle of Fig. 18 A.

When more than two cylinders are needed in a motor according to this synchrone principle, more cylinders may be added, so that e.g. another 2^nd enclosed space may be connected to the not yet used end for a connection to the 2^nd enclosed space of the added cylinder, so that a 3 -cylinder motor is created. The then still free 3^rd enclosed space of the added cylinder may be connected to a 3^rd enclosed space of another added cylinder, so that the motor may function with 4 cylinders. The now shown closed ends of the channels of the sub-crankshafts may need than to open up to establish communication between enclosed spaces with equal pressure schemes. Fig. 19B left shows an enlargement of the left part of Fig. 19B.

Fig. 19B right shows an enlargement of the right part of Fig. 19B.

Fig. 19C shows a two cylinder motor, based on Fig. 19A, which is in pressurisation process comparable to Fig 19B. Fig 19C depicts that the configuration of a motor with synchronous operated pistons may be differing from a motor where the pistons are installed in the same direction (0°). In the configuration of Fig 19C the power strokes of the piston actuators occur at the same moment, but the orientation of the actuator piston 800L is rotated over 180°. Said re-orientation is both in the connection to the crankshaft as in the direction of the conical chamber, where the piston actuator is moving in, and consequently the power stroke is oriented in the opposite direction. Each second enclosed space in the sub-crankshafts' is connected to the pressure storage vessel by channel [829] and the enclosed spaces are corrimunicating with each other by external channel [825]. The third enclosed spaces are communicating with each other via the external channel facilitating the flow from the actuator pistons to the piston pump. At the connection of the two sub-crankshafts, the enclosed spaces are interrupted and there is no communication between the piston assemblies 800L and 800R.

Fig. 19C left shows an enlargement of the left part of Fig. 19C.

Fig. 19C right shows an enlargement of the right part Fig. 19C. Fig 19D shows a two cylinder motor, based on Fig. 19 A, where the piston actuators run asynchronous. When piston assembly 800L starts with the return stroke, piston assembly 800R starts with the power stroke. Consequently, one piston actuator is in the second longitudinal position when the other piston actuator is at the first longitudinal position, and vice versa. The orientation of the actuator pistons is in opposite direction ( 180°). As there is at every moment a power stroke and a return stroke, the power supply by the motor of 19D is continuous and of a rather constant level. The enclosed spaces of each cylinder assembly are not connected via the sub-crankshafts, the pressurisation channel [829] commumcates with both second enclosed spaces. The channel [825] between the third enclosed spaces communicates also to piston pump 826. Because the openings in the connector from the second or third enclosed space to the actuator piston are differing half a cycle between piston assembly 800L and 800R, the communication by the pressure channels between the piston assemblies is limited to the enclosed spaces. As there is no communication through the connections between the sub-crankshafts the channels [825] and [829] are external.

Fig. 19D left shows an enlargement of the left part of Fig. 19D.

Fig. 19D right shows an enlargement of the right part Fig. 19D. Instead of toothed belts at the power side of the motor, there where the pump(s) are being driven, may very well be exchanged by gear.

19620 DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 21 A shows a so-called constant maximum force chamber 1 , with a wall part 2 of the longitudinal cross-section, at a first longitudinal position of the piston (not shown), which is parallel with the centre axis 3. A part 4 of the chamber wall has a convex formed wall of the longitudinal cross-section of the chamber 1. A transition 5 of the longitudinal cross-section of the outside wall of the chamber from convex wall parts 4 to concave wall parts 7. The wall part 6, which is positioned at a second longitudinal position of the piston (not shown), is not parallel to the centre axis 3 of the chamber 1. Common border 9 of a longitudinal cross-sectional cross-section 10 of the chamber 1 at a longitudinal position where 1 Bar overpressure has been reached by the piston (not shown), when moving from a first to a second longitudinal position. The common borders 11 / 13 / 15 / 17 / 19 / 21 / 23 / 25 and 27, respectively, between the longitudinal cross-sectional sections 12 / 14 / 16 / 18 / 20 / 22 / 24 / 26 / 28 / 30 of the chamber 1 at a longitudinal position where 1 / 2 / 3 / 4 / 5 / 6 / 7 / 8 / 9 / 10 Bar, overpressure over atmospheric pressure, respectively in e.g. an advanced bicycle pump has been reached by the piston (not shown). The internal walls of longitudinal cross- sectional sections 28, 29, 30, 31, 32, 33, 34, 35 and 6 are convex shaped, while the internal wall of longitudinal cross-sectional section 7 is concave shaped (between 6 and 7 Bar overpressure) for a 10 Bar (overpressure) pump. Dashed is shown the outside shape (36-37- 38) of the chamber if slavishly the mathematical equation had been followed - this is done for design purposes, so as to avoid that the chamber is looking top heavy. This adaptation as such has no influence on the max. working force, because it has been done in the beginning of the hyperbolic function (working force on the piston as a result of the shape of the chamber in a longitudinal direction, measured from a first to a second longitudinal position). Due to the small and constant size of the wall thickness over the total length of the chamber is this also the case for the external walls of said longitudinal cross-sections (not numbered): please see WO/2008/025391.

The longitudinal positioning of said common borders may be mathematically determined as a result of the rest volume of the stroke volume of a conical chamber under the piston, and its maximum value of the pressure, which is in this figure: 10 Bar. Characteristic is that the distances between said common borders which follow each other counted from a first longitudinal position of the piston to a second piston positions are decreasing the higher the overpressure rate is. That is than also the case for the heights of the respective walls of said longitudinal cross-sections sections 28, 29, 30, 31, 32, 33, 34, 35, 6 and 7. The positions of the wall at said common borders is based on a chosen value of maximum working force - which is in this case 25 kgf (250 N). The result is the characteristic shape 1 of the chamber (WO/2008/025391).

Fig. 2 IB shows the shape 1 (continuous line) of the 10 Bar (overpressure) chamber of Fig. 21 and the shape of a 16 Bar (overpressure) chamber (dashed) for the same length of the chamber. If the transitional size of the internal diameter of the part 30 would give problems for the size of the piston, may a recalculation of the sizes of the chamber may be done, by enhancing the maximum value of the working force, by an unchanged maximum value of the overpressure. This will make the diameter of e.g. reference number 30 bigger. The wall thickness is approximately even over the length of the chamber, although at said concave part 7 the thickness might be a bit bigger than the wall thickness of the rest of the wall. Another recalculation may be done, if the maximum overpressure should be bigger than 10 Bar, e.g. 16 Bar. This may be accomplished by choosing a higher maximum work force, so that the circumference of a transversal cross-section may become bigger. This means that the conical shaped outer wall of the chamber can go nearer 2^nd longitudinal positions, before the circumference reaches its minimum value in order to ensure, that a piston would not jam, which is defined by the piston type. Near first longitudinal positions would following verbatim the calculations, the size of the chamber would become too big, and that is why, one may define its shape there, so that the circumference becomes smaller - this may also be the case for other common borders as well.

A task to optimize the chamber to demands toward handpumps can be done in similar ways, as those described above. The problem here to be solved is a good compromise between the minimum size of the circumference of the inner chamber wall (depending on what a piston can perform) and the max. circumference of the outside of said chamber at first longitudinal positions, which is where a user is holding the handle, and the designated maximum working force.

Fig. 22A shows a bottom part of a chamber of an advanced bicycle floor pump where also the bottom part of the chamber 1 of Fig. 21 can be seen. The chamber 1 is mounted on a foot 41. A flexible manchet 42 assembles the chamber 1 on the foot 41. The hose 43, which is connected to the exit 44 of the pressure expansion vessel 49 - this exit is without a check valve. The (schematically drawn) piston 45 is comprising a piston rod 46. At the bottom of the piston rod is a check valve 47 positioned, which is communicating with the external atmosphere (48), and is opening towards the chamber 1, so as to fill the chamber 1 when the piston 45 is moving from a second longitudinal position to a first longitudinal position. An expansion pressure vessel 49 with a chamber 56 is shown, comprising an inlet check valve 50, when open, the chamber 1 is communicating with the hose 43, through an exit 44. The cross-section of the external wall 51 of the expansion pressure vessel 49, with an internal wall 52. The expansion pressure vessel 49 is assembled between a top end 53 and a bottom end 54 of said vessel 49. The top end 53 of the expansion pressure vessel 49 is sealed to the wall of the chamber 1 by an O-ring 55, while the top end 53 and the bottom end 54 are sealed to the wall 52 of the expansion pressure vessel 49 by gas sealing thread 58 and 59 respectively.

This is a preferred embodiment for very high pressures (e.g. 16 Bar), and if the piston has difficulties in sealing to the internal chamber wall. This construction avoids the sealing on the transition from a longitudinal cross-sectional section with a convex wall to a longitudinal cross-section section with a concave wall - please see Fig. 1.

Fig. 23 shows another constant force chamber 80 for a maximum pressure of 10 Bar with the same specification as the chamber of Fig. 1, with the exception that it has to secure that a pressurized container type piston has to be non-moving on a second longitudinal piston position - the internal wall 81 of the chamber at said second longitudinal piston positions should be chosen and shown being parallel to the centre axis of the chamber:

The transition from said convex walls 82 of longitudinal cross-sectional sections between common borders 83 and 84, corresponding to 0 Bar and 7 Bar overpressure, respectively to said wall 81 parallel to the centre axis 85 of the chamber 80 has a special internal concave shape 86, comprising smaller inner concave shaped subsections 86.1, 86.2 and 86.3 respectively, between a common border 84, which corresponds to 7 Bar overpressure until the common border 88 for 10 Bar overpressure. The shape of the inside wall of said chamber and its outside wall may not anymore correspond to each other: between the common border 84 for 7 Bar overpressure and the common border 88 for 10 Bar overpressure is the outside wall is still convex, while the inside wall is concavely shaped. This difference in shape, makes it possible to increase the wall thickness in relation to that of the rest of the wall thickness of the chamber, there where the chamber has its weakest spot: the transition from concave internal wall sections to the inside wall parallel to the centre axis of said chamber. The external wall 89 of the chamber, which is positioned there where the internal wall of said chamber is parallel to the centre axis of said chamber may be chosen as a straight line, but not necessarily parallel to said centre axis. This may be done for a good looking purpose, as curved shapes give some visual tension.

The transition from concave inside walls to said inside wall of said chamber which is parallel to the centre axis of the chamber may be made smoothly, in order to be able to let a piston pass this transition, without jarnming.

Fig. 24 shows the foot 70 of an advanced floor pump for e.g. tyre inflation. The flexible manchet 71 keeps the cone formed chamber 80 of Fig. 3 in place. The inside wall 81 of the chamber 80 is parallel to the centre axis 85 of the chamber 80. The inflatable piston 73. The enclosed space 66. The tube 65. The inlet check valve 75. The outlet check valve 76. The hose 77. The measuring space 78, 79 (inside the hose). The valve connector 67 (not shown). The space 68 inside the valve connector 67 is also part of the measuring space (not shown).

Fig. 25 shows chamber 100, which is a 10 Bar overpressure chamber of the chamber 1 of Fig.21. It's second longitudinal positions end with a common border 27. This bottom of this chamber is screwed on a bottom part 101 which is corresponding the longitudinal cross- sectional section 30 of Fig.21. The thread connecting both parts of the chamber is gas thread 102, which makes a gas tight connection. In the bottom 103 of chamber part 100 is an exit 104, in which a hose nipple 105 has been screwed. The chamber part 100 is comprising a piston 106, which has been schematically drawn. The piston 106 is comprising a hollow piston rod 107, which is comprising a check valve 108, which opens the space 109 between the piston and the bottom 103, and thereby let air in from the atmosphere (48) into said space 109. On the hose nipple 105 is a hose 110 assembled with a hose clamp 111. The hose is at its other end connected to e.g. a valve connector 67. The hole 112 in hose 110.

19630 circular chamber design

DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 30A shows the circular chamber of Fig. 12B, where a piston is moving in a non- moving chamber. A circular sub-chamber 961 is having a centerpoint 980 for the circleround section line 981 closest to the centerpoint 967 of the circular chamber 960, in an earlier quadrant 982 than the quadrant 983 wherein said line 981 is lying. The radius line 987 between the circle centre 980 and the circle section line 981. The circleround section line 984 of the circular sub- chamber 961 farthest to the centerpoint 967 of the circular chamber 960 is having a centerpoint 985 in a later quadrant 986 than wherein the line 984 is lying. The radius line 988 between the circle centre 985 and the circle section line 984. This may be valid for all the other sub-chambers 962, 963 and 964. The said circleround section lines may be circular section lines in other preferred embodiments.

Fig.31A shows the Fig. 14D, where the section X-X has shown, of said chamber 1749, and through the center axis 1750.

Fig. 3 IB shows an scaled up detail of section X-X of chamber 1749 of Fig. 31 A. The chamber wall 1785 is shown in the section X-X. The wall 1785 is comprising ducts 1786, 1787, 1788, 1789, 1790, 1791, 1792, 1793, 1794, 1795, 1796, and 1797, respectively which have an opening towards the chamber 1749. Preferably there is no duct approximately where the section

X-X is hitting the cross-section farthest from the center 1750 of the circular chamber 1749.

From there, around the circumference of the chamber 1749, from both sides (1786/7/8/9/90/91, and 1796/5/4/3/2/1) of the line of section X-X are ducts with increased width: the duct 1791 has the biggest width. Said ducts are meant to reduce the size of the contact area of the wall 1785 of the chamber 1749 with the piston, so as to steer the piston through the circular chamber, in the direction of the circular chamber, and to get an adequate propulsion force, which may be equal around the circumference of the contact area of a piston inside said chamber 1749 and the wall 1785, due to said ducts.

Fig. 32A shows the wall of the chamber and the orthogonal plane to the base circle intersects in a circle whose center is at the base circle.

Fig. 32B shows a section of the boundary of the piston. Fig. 32C shows the cap geometry - for area and internal volume of the cap we need values of a and h only - see formulas (2.1) and 2.2) - the radius of the virtual sphere is given in (2.3).

Fig. 32D shows the piston with end caps.

Fig. 32E shows the piston with end caps inside a transparent Fermi tube hamber.

Fig. 32G shows the contact area between the piston and the chamber.

Fig. 32H shows a section of the chamber wall. The chamber reaction force is marked by gray (1800). The total force on the section is orthogonal to the chamber wall. For the section is the value of the force proportional to the (variable) longitudinal length of the shown section, and to the internal pressure of the piston.

The local reaction force from the chamber wall is proportional to the longitudinal width of the section, which again is linear in the distance to the center of the center circle, i.e. the origin. To first order the length varies around the section as in a tube of constant radius. Said length depends linearly on the distance to the origin. The local force varies correspondingly and hence it is coordinated to drive the full wall and hence the piston as a pure rotation around the origin. The Fermi construction. The generator circle has at each point an orthogonal plane as shown. The chamber wall intersects every such orthogonal plane in a circle which has its center at the generator circle. The chamber wall is 'conical' when choosing the radius of said circle in the orthogonal plane to have a linear (or just increasing) value as function of arc length along the generator circle.

Fig. 321 shows the section of Fig. 32H, with an additional section in order to provide an open view.

Fig. 32J shows Fig. 32H, and the red (1801) vector is the component of the gray force (1800) in the longitudinal direction.

Fig. 32L shows Fig. 32J, where the actual sliding force along the wall is shown in blue (1802) - it is obtained by projecting the red (1801) vector orthogonally to the chamber wall.

Fig. 32M shows Fig. 32L, with an additional section in order to provide an open view. 19640 DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 40 A shows a longitudinal cross-section of a pump 1500 with a piston 1501 comprising U-formed support means 1502, an O-ring 1503 and a flexible impervious layer 1504, the last mentioned supported by a foam 1505 at a first longitudinal position of a chamber 1506. The support means 1502 are being rotatably fastened to the piston rod 1507 with the suspension 1508, comprising an axle 1510. The pulling spring 1509 is being fastened to the piston rod 1507 above the axle 1510, and at the other end on the support means 1502 closer to the O-ring 1503. The horizontally positioned spring 1511 is supporting the O-ring 1503. The impervious flexible sheet 1504 is comprising a layer 1512 with reinforcements 1514 (only shown in Fig. 40B, 4 ID, 4 IE), which has been vulcanized on a layer without reinforcements 1513. The centre axis 1518 of the chamber 1506. The angle a between a line which is connecting the centre of the axle 1510 with the centre of the O-ring 1503, with the centre axis 1518. The impervious flexible sheet is, unstressed by a loading from the fluid in the chamber 1506, perpendicular the centre axis 1518 of the chamber 1506.

Fig. 40B shows the^" impervious flexible sheet 1504 is vulcanized in the O-ring 1503.

The layer 1513 without reinforecements and the layer 1512 with reinforcements 1515, vulcanized on each other. The support means 1502 and the horizontal spring 1511 have been vulcanized on the O-ring 1503, and the impervious sheet 1504's layer 1513. The end of the support means 1502 has a small bended flat surface 1516, which fits the shape of the O-ring 1503 when produced. The O-ring 1503 is being squeezed on the wall 1517 of the chamber 1506.

Fig. 40C shows a longitudinal cross-section of the piston of Fig. 40A at a second longitudinal position. The piston rod 1507, the centre axis 1518 of the chamber 1506, with the wall 1517. The support means 1502 have been rotated around the axis 1510. the foam 1505' has been squeezed. The spring 1509' has been pulled longer. The O-ring 1503 has been increase in size, and is still squeezed to the wall 1517 of the chamber 1506. The impervious sheet 1504' has been increased in thickness, while the horizontal spring 1511 ' has been squeezed together. The angle β between a line which is connecting the centre of the axle 1510 with the centre of the O- ring 1503, with the centre axis 1518.

Fig. 41 A shows top view of the piston 1501 of Fig. 40 A and a cross-section of the α - 43"

β ~ parallel to the centre axis

* the foam may comprise stiffeners, which may be rotatably fastened to the piston rod, chamber 1506 from a first longitudinal position. The wall 1517 of the chamber 1506. The piston rod 1507. The suspension 1508 of the support means 1502. The axle 1510. The pulling spring 1509 of the support means 1502.

Fig. 41 B shows a detail of the suspension of the support means 1502 on the O-ring 1503 and the lying spring 1511 of the piston 1501 of Fig. 40A. The small bended flat surface 1516 at the end of the support means 1502, which is vulcanized on the O-ring 1503. The end 1519 of the support means 1502 has a notch 1521, which fits with its size and shape of the horizontal lying spring 1511. The boundary 1520 of the lying spring 1511 - said spring is only partially shown, at the end of the support means 1502.

Fig. 41C shows a cross section of the chamber 1506 with the piston 1501 of Fig.

40A at a second longitudinal position. The suspension 1508 of the support means 1502.

Fig. 41D shows spiral reinformcements 1522, 1523, 1524 of the flexible impervious sheet 1504 — the material is flexble. These spirals are drawn approximately concentrically to each other, on a certain distance, around the centre axis 1518 of the chamber 1506. Other configurations, e.g. two layers with reinforcements which may cross each other with a small angle, may be possible, but not shown.

Fig. 41 E shows another reinforcement configuration, namely more or less elastically reinforcement members 1525, lying concentrically around the centre axis 1518 of the chamber 1506.

Fig. 42 A shows a longitudinal cross-section of a piston 1530 comprising support means 1502, an O-ring 1503 and a flexible impervious sheet 1531, the last mentioned at a certain angle λ with the centre axis 1518 of the chamber 1506, at a first longitudinal position. Said sheet 1531 is being vulcanized (1532) on the piston rod 1507. The angle a between a line which is connecting the centre of the axle 1510 with the centre of the O-ring 1503, with the centre axis 1518. The flexible impervious sheet 1531 has an angle γ with the centre axis 1518 of the chamber 1506.

Fig. 42B shows a detail of the suspension of the support means 1507, O-ring 1503 and the flexible impervious layer 1531, vulcanised together. The top layer 1533 is comprising the reinforcements (as those of Figs. 41D-E), while the bottom layer 1534 has no reinforcements. The angle β between a line which is connecting the centre of the axle 1510 with the centre of the O-ring 1503, with the centre axis 1518.

180^ο - γ ~ 110° ( > 90° ) Fig. 42C shows a longitudinal cross-section of the piston 1530 of Fig. 42 A at a second longitudinal position. The angle ξ between the flexible impervious sheet 1531 and the centre axis 1518 of the chamber 1506.

180°-ξ~95^ο(>90°)

19650 DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 50 shows a top view of the holder 1224, and the suspension in the three rows of holes 1240, 1241 and 1242, respectively of the stiffeners 1208, 1209 and 1210, respectively in said holder 1224. The small bended ends 1220, 1221 and 1222, respectively. Please note that the longer the stiffener 1208, 1209 and 1210, respectively, the longer said small bended ends 1220, 1221 and 1222, respectively are, the longer the stiffeners are. The hole 1243 of the piston rod (not shown). The centre axis 1244. The foam 1245 of said piston 1200.

Fig. 51 shows a piston 1200 of Fig. 50 build in a pump 1201 with a chamber 1202 and a top 1203 and shown ata first longitudinal position 1204 of said chamber 1202. In the top 1205 is a bearing 1206, in which a piston rod 1207 is moving. The bearing 1206 is assembled in said top 1203. The chamber 1202 is of a type where the force is independant of the pressure (see 19620). The wall 1207 of said shamber 1202. All stiffeners 1208, (1209 dashed) and 1210, respectively have a free end of increased diameter 1211, (1212) and 1213, respectively. The impervious layer 1214, which is closed by a clamp 1215 to the piston rod 1207, while at the top 1216 of the piston 1200, the foam can communicate with the fluid in the chamber 1202, at the non-pressurized side 1202'. The stiffeners 1208, (1209) and 1210 having a bend 1217, (1218), 1219, repectively and a small bended end 1220, (1221) and 1222, respectively. Said small bended ends 1220, (1221) and 1222, respectively may be pressed by an adjustment member 1223, which can turn within a holder 1224, which is sealed by an O-ring 1227 to the piston rod 1207. Said adjustment member 1223 is rotatable in said holder 1224, and sealingly connected to said impervious layer 1214. The piston 1200 is assembled onto the piston rod 1207 by the holder 1224 being mounted within a spring ring 1225 while the clamp 1215 being mounted to the spring ring 1226. The centre axis 1243 of the chamber 1202.

Fig. 52 shows the bend 1218 of the stifener 1209. The increased diameter 1212 of stiffener 1209. The chamber 1202. The end 1221.

19650-1 DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 55 A shows a piston 1300 at a 1^st longitudinal position of an advanced pump, said piston 1300 is comprising a foam 1301 with metal reinforcement pins 1302, 1303, 1304 positioned in three circular rows around the piston rod 1306, in a direction towards the pressurized side of said piston 1300, which are fastened by magnetic force to a magnetic holder plate 1307 of a holder 1308, which is mounted on the piston rod 1306, and an impervious layer 1305 around said foam 1301. Said holder plate 1307 has been mounted on a holder 1308, glued or by other means. Said holder 1308 may be able to rotate around the piston rod 1306, and is fastened in the longitudinal direction to said piston rod 1306 by two spring plates 1310 and 1311, which fit in notches 1312 and 1313, respectively of said piston rod 1306. The metal of said pins may be magnetized. The foam 1301 may made of open cells, preferably PU foam (as discussed in section 19650 of this patent aplication) - the venting of said open cells is being discussed in Fig. 55B. The holder 1308 has a gland 1317 for an O-ring 1318, which is sealing said holder 1308 to the piston rod 1306. The centre axis 1319 of the piston 1300. The impervious layer 1305 may be made of natural rubber (NR), and the production size and shape is that of the size and shape of the outside of said piston 1300', when positioned at a 2^nd longitudinal position of the chamber (not shown). That is to say, that said impervious layer 1305 is expanding when the piston 1300' is running towards a 1^st longimdinal position, by the forces of the expanding foam 1301. Said reinforcement pins 1302, 1303, 1304 may have a thin layer of PU (not shown), which makes that the PU foam better hold on said pins 1302, 1303, 1304. This surface treatment may be done by e.g. dipping said pins 1302, 1303, 1304 in PU foam fluid. The arrow 1335 shows how the foam is being squeezed towards the piston rod 1306 when the piston 1300 is running towards the 2^nd longitudinal position where the piston has the reference 1300'. The low pressure side 1315 of the piston 1300, and the atmosphere 1316.

Fig. 55B shows an enlargement longitudinal cross-section P-P of the holder plate

1307, mounted on said holder 1308. The centre axis 1325 of said holder 1308. The holder plate 1307 has been made of magnetic material, e.g. by compressing metal powder, and backing it thereafter. On top of the holder 1308 are venting channels 1314 with centre axis 1321 (see also Fig. 55C), through channel 1320 the holder plate 1307 (please see Fig,55C), enabling a communication of a fluid within the open cells to and from the non-pressurized side 1315 of said piston 1300 to the atmosphere 1316 near said non-pressurized side 1315. This construction is also used in Figs. 55E-H (incl.). Fig. 55C shows an enlargement of the holder plate 1307 on the holder 1308. The underside of said holder plate is comprising three rows 1326, 1327, 1328 of small closed, rounded off end holes 1329, 1330, 1331, respectively, in which the ends of the metal pins 1302, 1303, 1304 of Fig. 55 A are being hold. Said ends may be rounded off, so that these fit better in said end holes 1329, 1330, 1331, respectively. The rounding off of said end holes, and the sides of the 'log' holes - the radius is a little bit bigger than the diameter of said pins 1302, 1303 and 1304, respectively (not shown in this drawing) - enables said pins 1302, 1303, 1304 to rotate in a plane which is comprising the centre axis of the holder 1308. The centres of rounded off end holes lay all in a plane perpendicular the centre axis of the holder 1308. The left side of said end holes 1329, 1330 and 1331 is not as deep as the right side of each hole, in order to guide the top of the respective pins 1302, 1303 and 1304, respectively to the rounded off sides of said end holes 1329, 1330 and 1331, respectively. Between the holder 1308 and the holder plate 1307 is a small circular reces 1332 of the holder 1308, which enables the impervious layer 1305 to be squeezed between the holder 1308 and the holder plate 1307, when the holder plate 1307 is fastened by e.g. screws (not shown) to the holder 1308.

Fig, 55D is showing an enlargement of the protuberance 1333 in said reces 1332, for an improved squeezing of the impervious layer 1305 (not shown). This construction is also used in the embodiments of Figs. 55E and Fig 55G, enlarged shown in Figs. 55F and 55H, respectively.

Fig. 55E shows an alternative solution to the one shown in Figs. 55A-D. The new reinforcement and the fastening of the foam 1351 (not shown) of the piston 1350 (not shown) to the holder 1359 have been shown in detail in Fig. 55F. Said piston 1350 is positioned at a 1^st longitudinal position of an advanced pump. The venting channels 1314 are indentical with those described in Figs 55B and 55C.

Fig. 55F shows an enlargement of the holder plate 1358 and the holder 1359. Said piston 1350 is comprising plastic pins 1352, 1353 and 1354, respectively, as reinforcement of said foam, preferably made of the same material as the foam - preferably PU as described in Fig. 55A - which are rotatably fastened with their sphere shaped ends 1355, 1356 and 1357 into sphere cavities 1360, 1361 and 1362, respectively of said holder plate 1358, which is mounted on a holder 1359, the last mentioned is mounted on a piston rod 1306, as discussed in the description of Fig. 55 A. Said holder plate 1358 is additionally comprising further openings 1363, 1364 and 1365, respectively for guiding said pins 1352, 1353 and 1354, respectively. Said pins 1352, 1353 and 1354 may have an uneven thickness in order to better hold said foam. An optimized configuration may be that the thickness uneveness firstly begin a bit further from the sphere shaped ends 1355, 1356 and 1357 than shown in the drawings, in order not to squeeze the foam between said pins 1352, 1353 and 1354 near said sphere shaped ends too much, when said pins 1352, 1353 and 1354 turn anti-clockwise, and come nearer each other, when the piston 1300 is running to a second longitudinal position. Please see Figs. 55C and 55D for the description of the fastening of the impervious layer 1305 between the holder 1359 and the holder plate 1358.

Fig. 55G shows an alternative solution to the one shown in Figs. 55E and 55F with holder 1365 and reinforcement pins 1366, 1367 and 1368.

Fig.56H shows an enlargement of said holder 1365 which is comprising a holder plate 1369 and a circular disk 1370 which is made of flexible material. The reinforcement pins 1366, 1367 and 1368 are similar with the pins shown in Fig. 56E and 56F, with the exception, that the pins 1366 and 1367 (and possibly also 1368 - but not shown here) are comprising each a pin 1371, 1372 (and 1373 - not shown) which each are connected to the sphere ends 1355, 1356 (and 1357). Said pins 1372 and 1372 are sticking into the elastic disk 1370, and make the pins 1352, 1353 and 1354 to automatically turn clockwise, when the piston is running to a 1^st longitudinal position.

19660 DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 60 shows the enlarged container type piston 1400, in a chamber 1401, which has a centre axis 1402, at the start and end of a stroke. The chamber is of a type where the force on the piston rod is approx. even dureing the stroke. The shape of the piston at a second longitudinal position is that of a 'starting' ellipso^'ide 1403 after having been pressurized from a non stressed production model, where the shape is approximately cylinder like shaped (see Figs. 61 and 62). The shape of the piston near a first longitudinal position is an ultimate ellipso'ide 1404, which is almost a sphere 1405 (dashed). In between has the piston 1400 the shape of an ellipso^'ide. The details of an ellipsoide instead of a sphere at a first longitudinal position are identical with these of a sphere.

Fig. 61 shows an unstressed produced container type piston 1400, which, stressed may have the shape of an ellipso^'ide or a sphere. At the bottom of the figure the non-movable cap 1420, with a gland 1421 for a 0-ring(not shown), which tightens on the piston rod (not shown). A recess 1422 which is more or less a gland for an O-ring (not shown), which tightens the bottom of the piston 1400 on a bolt (not shown) which locks the bottom of the piston rod (not shown), through the hole 1432. On top of the figure the movable cap 1423, which is -movable on the piston rod (not shown). The gland 1424 for an O-ring (not shown), which makes the piston tight in the top of saud piston 1400. Both caps 1420 and 1423 having a recess 1425 and 1426, respectively, which is used to vulcanize the flexible wall 1427 of the container piston 1400 on said cabs 1420 and 1423, respectively. Said wall 1427 is shown in the figure with two layers: a reinforced layer 1428 and a layer which functions as a cover 1429 for the reinforced layer 1428. The dashed lines show a possible third layer 1430 and 1431 , on top of the other layers 1428 and 1429, respectively, which is only present on the position where said two layers 1428 and 1429, respectively have been vulcanized on the cabs 1420 and 1423. The centre axis 1433. The wall 1427 of the piston 1400 is approximately parallel with the centre axis 1433. The reinforcement strengs 1440 lie in a parallel pattern, parallel to the centre axis 1433. The reinforcement pattern 1441 when there are two layers.

Fig. 61 shows both cabs 1420 and 1423, respectively of Fig. 61. At the outer side the rounded off transition 1434 and 1435, respectively, from the flexible wall 1427 to the portions of said wall 1427 which has been vulcanized on the portions 1425 and 1426 of said cabs 1420 and 1423, respectively. At the inner sides of the flexible wall 1427, just before said flexible wall 1427 meet the portions 1425 and 1426 of said cabs 1420 and 1423, respectively is a rounded off transition 1436 and 1437. These transitions 1436 and 1437 provide a stable transition of the wall, when the piston is being stressed by inflation. 19660-2 DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 63 shows the forces from the wall of an actuator piston (not shown) to the wall 2275 of a chamber 2276 with differing cross-sectional area's and differing or equal circumferences, and having a centre axis 2277. The reaction force 2278 perpendicular to the wall 2275 to the expansion force of the wall of the actuator piston (not shown - please see Fig.64A). The friction force 2281 from the actuator piston, during rolling, and specifically when sliding of the wall of said actuator piston (not shown - please see Fig. 64A) over the wall 2275 of the chamber. The reaction force 2279 of the wall 2275 of the chamber 2276 of the wall of the actuator piston (not shown - please see Fig. 64A). The component 2280 of said along the wall 2275 of said chamber 2276. Said component 2280 has been shown bigger that the friction force 2281. The angle a between the wall 2275 of the chamber 2276 and the centre axis 2277 of said chamber 2276.

Fig. 64A shows an ellipsoide type actuator piston 2285 in a chamber 2286 with a

longitudinal centre axis 2287, of which the wall 2287 of said chamber 2286 has an angle β with the centre axis 2288 and is drawn at a 20° angle. The wall 2289 of said actuator piston 2285 is engagingly connected to the wall 2287 of said chamber 2287.

Fig. 64B shows an ellipsoide type actuator piston 2290 in a chamber 2291 with a

longitudinal centre axis 2292, of which the wall 2293 of said chamber 2291 has an angle γ with the centre axis 2292 and is drawn of 10°. The wall 2295 of said actuator piston 2290 is engagingly connected to the wall 2293 of said chamber 2291. Said actuator piston 2290 is shown on three positions 2296, 2297 and 2298 in said chamber 2291, evidencing that it is possible to use said angle in a e.g. a car motor according this invention, having a stroke length of 86.4 mm (as a 1595cc petrol motor of a Golf Mark II), of comparable dimensions as said current petrol motor.

19680-2 DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 80 A shows a chamber 2101 of a pump according to section 19620 (however any other chamber configuration may be used), with a central axis 2102, and a wall 2103 of said chamber 2101, with a piston 2104, 2104' and 2104" according to section 19660, which may e.g. be inflatable, on three different longitudinal positions (1^st, middle and 2^nd, resp.), the wall 2105 of said piston 2104 is comprising a separate part 2106, of which the cross-section is circle segment shaped, which adapts its position to the slope a of the wall 2103 of said chamber 2101 and the centre line 2102.

Fig. 80B shows a scaled up (5:1) detail of the contact surfaces 2107 of the wall 2103 of the chamber 2101, and 2108 of the wall 2105 of the piston 2104, respectively, when said piston

2104 is in a first longitudinal position, over which last mentioned surface 2109 said surface 2108 of the separate wall wall part 2106 can roll and slide. Said contact surfaces 2107 and 2108, respectively are sealingly connected to the wall 2103 of the chamber 2101 and to an inclined wall part 2109 of the said piston wall 2105, said inclined wall part 2109 has a smaller minimum circumference than that of the adjacent piston wall 2105, closest to the wall 2103 of said chamber 2101. Clearly is shown that the surface 2105 of said piston 2104 is clear from the wall 2103 of the chamber 2101. The contact surface 2107 of said separate wall part 2106 with the wall 2103 of said chamber 2101 is comprising parts two surfaces 2110 and 2111, which have an angle b and angle c with the wall of said chamber, which at the contact surface 2108 of the wall 2103 are tightly squeezed to the wall 2103 of said chamber 2101, having the angle f of the chamber wall 2103 with the centre axis 2102. When the circumference of the piston 2104 is becoming bigger, the separate wall part 2106 may be squeezed towards the wall 2103 of said chamber 2101, while the rest of the wall 2105 of said piston 2104 is on tension, thereby retracting from its original (Fig. 80F) position. The transversal centre line 21 15 of said piston 2104. The centre line 2114 of the separate wall part 2106 through the middle 2116 of the contact point of the separate wall part 2106 and the wall 2105 of said piston 2104. The angle d between said transversal centre line 2114 and a line perpendicular the central axis 2102 of said chamber 2101.

The contact surface 2127, e.g. by vulcanisation of the circle part of the longitudinal cross-section of said separate wall part 2106 with the wall of said piston 2104, may be just a part of said circle segment near its transversal centre line 2114 of said separate wall part 2106.. The adjacent wall

2105 will than be able to bend more, which enables said separate wall part to remaining sticking out of the wall 2105, and arranging thereby a clearance with the wall 2103 of said chamber 2101 with the adjacent wall 2105 of said piston 2104, 2104', 2104". This may also be the case for the separate wall part 2123 shown in Figs. 80H, and the toroids 2207, 2244 of Figs. 84B and 84F, respectively. The circumference of said separate wall part 2106 will also be much bigger when the piston 2104 is on a 1^st longitudinal position than when said piston is on a 2^nd longitiudinal position.

Fig. 80C shows the separate wall part 2106 when the piston is in a second longitudinal position. Here is the wall 2105 of said piston 2104' still clear from the wall 2103 of the chamber 2101, but less than in the case of when the piston 2104' is in the first longitudinal position (Fig. 80B). The angle e between the transversal centre line 2114 and a line perpendicular the central axis 2102 of said chamber 2101. The transversal centre line 2115 of said piston 2104'.

Fig. 80D shows separate wall part 2106 of which the cross-section is circle segment shaped of the wall 2105 of said piston 2104", when the piston 2104 is in a second longitudinal position - its position within the circumference of said wall 2105 enables the piston 2104 to be in that part of a 2^nd longitudinal position of the chamber 2101, where its wall (not shown) 2103 is approximately parallel to the centre axis 2102 of said chamber 2101.

Fig. 80E shows an alternative sphere shaped separate wall part 2112 of that shown in

Figs. 80A-C. The advantage may be, that there may be relatively more clearance between the separate wall part 21 12 of said piston 2104" and the wall (not shown) 2103 of said chamber 2101, than in case of the circle segment shape of the separate wall part 2106 of Figs. 80A-C. The transversal centre line 21 17 of the separate wall part 2112.

Fig. 80F shows an alternative halfround shape of the separate wall part 2113 with a centre line 2114, which is identical with the transversal centre line 21 15 of said piston, shown in Figs. 80A-C. Said separate wall part has been vulcanized on a (scaled up) piston according to section 19660, when said piston 2104" is in a second longitudinal position, as produced.

Fig. 80G shows an improved version of the embodiment of Fig. 80F, where the transversal centre line 2120 of separate wall part 21 13 is positioned under a line 2121 through the longitudinal midpoint of the flexible wall of said piston 2104", so to ensure a proper contact area with the conical chamber, where the smallest cross-sectional area is at a second longitudinal position, i.e. nearest the part of said piston 2104" nearest the 2^nd longitudinal position.. Other chamber configurations may give another positioning of said separate wall part 2113 and its transversal centre line 2120.

Fig. 80H shows a longer piston 2126 (than the one shown in Fig. 80G) at a first longitudinal position, where the piston 2126 has been inflated. The centre line 2122 of the separate wall part 2123 is positioned under a transversal centre line 2124 through the longitudinal midpoint of the flexible wall 2125 of said piston 2126, so to ensure a proper contact area with the chamber (not shown). Other chamber configurations may give another positioning of said separate wall part 2106 on the wall 2125 of said piston 2126

Figs. 801 and 80J show a piston 2130 which has a decreased circumference at its transversal centre line 2131, as produced (thus at a second longitudinal position). The centre line 2132 of the separate wall part 2133, as-produced. This enables a better avoidance of contact of other parts of the wall 2134 of said piston 2130 than that of the separate wall part 2133, to the wall 2134 of the chamber 2136, specifically when said piston is moving from an extrimite 2^nd longitudinal position 2137 of the chamber as shown in Fig. 801 (according section 19620 of this patent application - however any other chamber configuration may be used), in the direction of a 1^st longitudinal position 2139 , when the wall 2134 of the chamber 2136 is changing from being parallel to the centre axis 2138 of said chamber 2136 to become non-parallel. The longitudinal centre line 2135 of said piston 2130.

Fig. 81 A shows a chamber 2101 of a pump according to section 19620 (however any other chamber configuration may be used), with a central axis 2102, and a wall 2103 of said chamber 2101, with an enlarged piston 2140 according to section 19660 e.g. according to Fig. 61, which may be inflatable, on three different longitudinal positions 2140, 2140' and 2140", the wall 2141 of said piston 2140, 2140', 2140" is comprising more than one, e.g. two separate wall parts 2142 and 2143, of which each longitudinal cross-section is circle segment shaped, which adapt its positions to the parallel- (extremite 2^nd longitudinal position), concave- (transition from extremite 2^nd longitudinal position to a position nearer a 1^st longitudinal position), and convex wall (from said transition to a 1^st longitudinal position), respectively of the wall 2103 of said chamber 2101.

Fig. 81B shows scaled up contact surfaces 2144 / 2145 and 2146 / 2147 for the separate wall parts 2142 and 2143, respectively, which are sealingly connected to the wall 2103 of the chamber 2101 at a 1^st longitudinal position and to the inclined parts 2148 and 2149, respectively of the said piston wall 2141, said inclined parts 2148 and 2149 have a smaller rninimum circumference than that of the adjacent piston walls, which are positioned closest to the wall 2103 of said chamber 2101. The separate wall parts 2142 and 2143 are positioned at a certain distance g from each other, in order to avoid that the wall 2141 of said piston 2140 is engaging and/or sealingly engaging with the wall 2103 of said chamber 2101. Depending on the slope e of the wall 2103 of the chamber 2101, is the separate wall part 2143 positioned closest to a first longitudinal position closer to the transversal centre line 2130 of said piston 2141 than the separate wall part 2142 positioned closest to a second longitudinal position. The position of the separate wall parts may different from the above mentioned, and depends on the shape of the piston 2140, 2140' and the slope(s) of the wall 2103 of the chamber 2101, with the goal to avoid a continuous curved wall of the piston, so as to avoid that the piston 2140, 2140' can roll over the surface 2103 of the chamber 2101.

Fig. 81C shows a scaled up detail of said contact surfaces when said piston 2121 is positioned between a first and a second longitudinal position. Also here is there no contact between the wall 2136 of said piston 2140' and the wall 2103 of said chamber 2101.

Please remark that the angles between a line perpendicular the wall 2103 of said chamber and the centre axis 2137 and 2138 of said separate parts - with a sloped wall 2103 of said chamber 2101, are said angles not identical, and bigger than those of Fig. 8 IB.

Fig. 81D shows said (scaled up 12.5:1) piston, which is positioned in an extremite second longitudinal position, as produced. As it is in Fig. 80D may the piston 2140" comprising the separate wall parts 2142 and 2143 be in said chamber 2101 (not shown), there where its wall 2103 (not shown) is parallel to the centre axis 2102 of said chamber 2101 (not shown). The arrow shows the transversal centre line 2130 of the piston 2140".

Fig. 82 A shows a chamber 2101 of a pump according to section 19620 (however any other chamber configuration may be used) with a longitudinal center line 2102, with a piston 2145 which may be inflatable, said piston 2145, 2145' and 2145"is shown on three different longitudinal positions, respectively, the piston wall 2146 is comprising two parts 2147 and 2148, respectively, having different circumferences in a transversal plane, where the part 2147 closest to the first longitudinal position is having the biggest circumference, and is comprising the contact area's 2149, 2149' and 2149", respectively between the wall 2103 of the chamber 2101 and the piston wall 2146. The size of said contact area's may be different on each of the three longitudinal positions.

Fig. 82B shows a scaled up (5: 1) detail of said contact area 2149 when said piston 2145 is in a first longitudinal position. The two piston wall parts 2147 and 2148. The piston wall part 2147 is comprising an outer skin part 2150, which is ending just under the contact area 2149, with a stepped transition 2199 of the wall 2146 from wall part 2147 to wall part 2148, where the piston wall part 2147 nearest a 1^st longitudinal position is closest to the wall 2103 of the chamber 2101, that the wall part 2148, which is nearest a 2^nd longitudinal position. Under said skin part 2150 may be another skin part 2151, preferably a layer, optionally a reinforcement layer. This skin part 2151 is preferably present in the whole piston wall 2146. Approximately (an overlap would be preferable) there where the outer skin part 2150 of the piston wall part 2147 ends, begins an inner skin part 2152, which is part of the piston wall part 2148, and which is positioned behind the outer skin part 2151. The content of said piston may be a fluid, a mixture of fluids or a foam (not shown). There is no contact between the skin part 2148 of the wall 2146 of said piston 2145 and the wall 2103 of said chamber 2101. The transversal centre line 2153 of said piston 2145, which is nearer a first longitudinal position than the stepped transition 2199 of the wall 2146 from wall part 2147 to wall part 2148.

Fig. 82C shows a scaled up detail of said contact area 2149 'when said piston 2145' is positioned between a first and a second longitudinal position. Also here is there no contact between the skin part 2151 of the wall part 2148' of said piston 2145' and the wall 2103 of said chamber 2101. Shown is that the contact area 2149' of the wall part 2147'wit the wall 2103 of said chamber 2101 may be different from the contact area 2149 of Fig. 82B. The transversal centre line 2153' of said piston 2145'. This centre line 2153' may be positioned closer to a 1^st longitudinal position that said stepped transition 2199 of the wall 2146 from wall part 2147 to wall part 2148.

Fig. 82D shows said (scaled up 12.5:1) piston 2145" of which the wall 2146 of said piston 2145" , which is positioned at a second longitudinal position - the chamber is not shown. The wall part 2147 has a diameter ø z, while the wall part 2148 has a wall part ø z-zi (z^O). The transversal centre line 2153" of the piston 2145". Fig. 83A shows the piston 2121 " of Figs. 82A-D (incl.), as produced in a 2^nd longitudinal position, and the piston rod 2151.

Fig. 83B shows the piston 2121 of Fig. 83A at a 1^st longitudinal position, where said piston 2121 is being inflated - arrow 2152 - through its piston rod 2151.

Fig. 83C shows the piston 2121 of Fig. 83B in a 1^st longitudinal position, where said piston 2121 is being deflated - arrow 2153 - through its piston rod 2151, after the position of the movable cab 2154 has been secured on the piston rod 2151, by a clamp 2155. Fig. 83D shows the piston 2121 of Fig. 83C in a 1^st longitudinal position, where the cavity (not shown) (2156) of said piston 2121 is being filled - arrow 2157 - through the enclosed space (2159) its piston rod 2151, with a foam (not shown) (2158). This foam may be of a PU foam (Polyurethan), preferably as a mixture of a Memory PU foam type (please see section 19640 of this patent application), and a standard PU foam type - this is a good compressible foam with an open cell structure.

Fig. 83E shows the piston 2121 of Fig. 83D in a 1^st longitudinal position, where the cavity (not shown) (2156) of said piston 2121 has been filled with said foam (not shown) (2158), after said clamp 2155 has been removed. It is now possible to compress the wall 2146 of said piston 2121, e.g. by moving said piston rod 2151 incl. said piston 2121 from a 1^st longitudinal position to a 2^nd longitudinal position, without much force.

It may be necessary to add a compressed fluid, such as a gaseous medium, through said foam's open cells, in order to achieve the proper sealing force and/or a proper compression force for said piston.

Fig. 83F shows said piston 2121 " with inserted and now compressed foam (not shown) (2158) of Figs. 83D and its piston rod 2151, and a combined pressure sensor 2160 and inflation valve 2161 according Fig. 3B of W02109/083274, for the enclosed space (2159) (not shown) + cavity (2156) (not shown) of said piston 2121 ". Said piston rod 2151 may preferably be of the type where its enclosed space (not shown) (2159) has a constant volume (W02110/094317), optionally a type with a variable volume according to WO 2100/070227.

Fig 83 G shows an enlargement of the combined sensor - inflation valve arrangement of Fig. 83F. The inflation valve 2161 with the inlet 2196 for the enclosed space 2159 of the piston rod 2151. The inlet 2194 of the pressure sensor 2160 and its outlet 2195 according to W02111/000578.

Fig. 83H shows said piston 2121" with inserted foam (not shown) (2158) of Figs. 83D and its piston rod 2151, and a combined pressure sensor 2162 and inflation valve 2161 according Fig. 5 of W02111/000578, for the enclosed space (2159) (not shown) + cavity (2156) (not shown) of said piston 2121 ". Said piston rod 2151 may preferably be of the type where its enclosed space (not shown) (2159) has a constant volume (W02110/094317), optionally a type with a variable volume according to WO 2100/070227. Fig. 831 shows an enlargement of the combined sensor - inflation valve arrangement of Fig. 83H. The inflation valve 2161 with the inlet 2196 for the enclosed space 2159 of the piston rod 2151. The inlet 2194 of the pressure sensor 2162 and its outlet 2197 according to W02111/000578.

Fig. 83J shows said piston 2121" with inserted foam (not shown) (2158) of Figs. 83D and its piston rod 2151, and a combined pressure sensor 2164 and inflation valve 2165 according Fig. 9 of W02111/000578, for the enclosed space (2163) (not shown) + cavity (2156) (not-shown) of said piston 2121 ". Said piston rod 2151 may preferably be of the type where its enclosed space (not shown) (2163) has a constant volume (W02110/094317), optionally a type with a variable volume according to WO 2100/070227.

Fig. 83K shows an enlargement of the combined sensor - inflation valve arrangement of Fig. 83 J. The inflation valve 2165 with the inlet 2198 for the enclosed space 2163 of the piston rod 2151. The inlet 2194 of the pressure sensor 2164 and its outlet 2199 according to W02111/000578.

The expansion to its default size of said PU foam cited in Fig. 83D, to blow up said wall 2146 of said piston 2121 - a spring 2166, which is pulling said movable cab 2154 towards the fixed cab 2167, is adding force for said expansion. Said spring 2166 is positioned over said piston rod 2151, and is attached to said movable cab 2154 and a fix 2168, which is positioned in a construction 2168 of said piston rod 2151.

In order to solve the problem that the volume of an inflated ellipso^'fde is much bigger than the volume of an small enclosed space, e.g. that of a piston rod, the inflated volume has been substantially reduced e.g. to an inflatable toroi^'d, while the expansion of the wall of the piston has been remained. This means that when an inflated piston is pushed from a 1^st longitudinal position to a 2^nd longitudinal position the rise of the internal pressure is small, enabling the piston to be depressed in size (without jamming).

Fig. 84 A shows an ellipsoide shaped type of piston 2170 at a 1^st longitudinal position (chamber not shown) having a centre axis 2171, and a piston rod 2172, a fixed cab 2173 and a movable cab 2174, on which both the elastically flexible wall 2175 of said piston 2170 has been mounted, e.g. by vulcanizing, said wall 2175 has a reinforcement layer 2176. Said piston 2170 has a wall of the type shown and discussed in Figs. 82A-D (incl). Said wall 2175 is has on the inside a U- shaped vault 2177, in which an inflatable toroid 2178 is positioned, which has a wall 2179 with an reinforcement 2180, so that the circumferencial size of said toroid 2178 is increased by a higher inside pressure, whithout change of its outer cross-sectional diameter d, and decreased by a lower pressure. This means that when said piston 2170 is at a 2^nd longitudinal position of a chamber (not shown), the wall 2175' of said piston 2170 is approximately parallel to the centre axis 2171, and said toroid 2178' is positioned adjacent said wall 2175 and said piston rod 2172, which has a constriction 2181, for giving space to said toroid 2178'. The wall 2179 of said toroid 2178 is much ticker than that when said piston 2170 is at a 1^st logitudinal position, having a reinforcement 2180 which having an angle more than 54° 44'. The flexible hose 2182 is through its channel 2190 communicating with the enclosed space 2183 of said piston rod 2172, and at the other end of said channel 2182 communicating with the channel 2184 within said toroid 2178. The U-shaped vault 2177 is guiding said toroid 2178 when said piston is moving between 1^st and 2^nd longitudinal positions. In order to lower the force which is necessary for the expansion of the wall 2175 of said piston 2170, when the piston 2170 is moving from a 2^nd to a 1^st longitudinal position, a pulling spring 2185 is postioned over said piston rod 2172, and attached to said moving cab 2174 and a hook 2186 which is fastened in said constriction 2181 of the piston rod 2172. Observe the small diameter of the channel 2184' inside said toroid 2178', when said piston 2170 is at a 2^nd longitudinal position of a chamber. The cross-section of the flexible hose 2182 with its channel 2190. Said channel 2190 is at one end communicating with the enclosed space 2183, and at the other end communicating with the channel 2184 and 2184'. The high pressure side 2187 of the wall 2175 of said piston 2170 is supported by a foam 2193 (e.g. PU foam of the kind disclosed in section 19630 of this patent application, and used in a foam piston) within the inside 2192 of the wall 2175 - 2187 of said piston 2170. Because said foam 2193 has open cells, it is communicating either with the enclosed space 2183 (not shown) or preferably with the low pressure side 2188 (not shown - or refer to Fig. 84B), optionally the high pressure side 2191 of said piston (not shown). Said toroid 2178, 2178' is shown having a centre axis 2194 which is converging with the transversal centre axis 2195 of said piston 2170, in order to gain an optimal ellipsoide shaped wall 2175. At the high pressure end of said piston rod 2172 is a pressure sensor shown which has been discussed in Figs. 83H/I.

Fig 84B shows a piston 2200 of an ellipsoide shaped type, which is an improved and simplified version of the piston 2170 of Fig. 84A, where the whole inside 2201 within the wall 2202 of the piston 2200 is comprising said PU foam 2203, discussed in Fig. 84A. Inside the wall 2202 of said piston 2200 is a channel 2205, mounted (e.g. by vulcanisation) on th inside of said wall 2202. Said channel 2205 is communicating with the channel 2206 of the toroid 2207 at one end , and at the other end the enclosed space 2208 of said piston 2200 in the piston rod 2209. The foam 2203 is communicating with the either the enclosed space 2208 through a channel (not shown), or it is communicating with preferably the low pressure side 2210 of said piston 2200 through a channel 2211 in the movable cab 2212, or optionally with the high pressure side 2211 of said piston 2200 (not shown). Said toroid 2207 is shown having a centre axis 2213 which is converging with the transversal centre axis 2214 of said piston 2200, in order to gain an optimal ellipsoide shaped wall 2202. However, as disclosed in Figs. 80A-C, H, where the contact surfaces 2107 and 2108 of said separate part 2106, with a centre axis 2114, were positioned closer to a second longitudinal position of the chamber, due to the shape of said chamber, than the the transversal centre axis 2115 of said piston 2104, 2104', 2104", so that said centre axis' 2114 and 2115 are not converging with each other. This may also be the case with the contact area of said toroid 2207 with the wall of the chamber (not shown), as it may also be positioned lower than the transversal centre axis 2214 of said piston 2200 (not shown here). At the high pressure end of said piston rod 2209 is a pressure sensor shown which has been discussed in Figs. 83H/I.

Fig. 84C shows the piston 2220 having the same construction of the piston 2170 of Fig. 84 A, with the exception of the wall 2221 on the low pressure side of said piston 2220. Said wall part 2221 is not a part of an ellipsoide as shown in Fig. 84 A, but that of a cone, shown in tension.

Fig. 84D shows a sphere shaped piston 2230 at a 1^st longitudinal position and 2230" at a 2^nd longitudinal position, having a longitudinal centre axis 2231, and a transversal centre axis 2232, 2232". Said piston 2230", 2230 is comprising a separate part 2231, 2231 " respectively with a transversal centre axis 2233, 2233". Said transversal centre axis 2233, 2233" is positioned under said a transversal centre axis 2232, 2232" and the first mentioned is positioned nearest a 2^nd longitudinal position. Other configurations of a separate part shown in Figs. 80A-E are also here possible.

Fig. 84E shows a sphere shaped piston 2235 at a 1^st longitudinal position and 2235" at a 2^nd longitudinal position, having a longitudinal centre axis 2236, and a transversal centre axis 2237, 2237", respectively. The stepped transition 2238 of the wall 2234 from wall part 2239 to wall part 2240. Fig. 84F shows a sphere shaped piston 2241 at a I^s longitudinal position and 2241 " at a 2^nd longitudinal position, having a longitudinal centre axis 2241, and a transversal centre axis 2243, 2243", respectively. Said piston 2241 is comprising a separate part 2244, 2244" with a transversal centre line 2245, 2245", respectively, the last mentioned is positioned under the transversal centre axis 2243, 2243" of said piston 2241, 2241 ", respectively, thus nearest a 2^nd longitudinal position. The inflation of the toroid 2244 may be done as shown in Figs. 84A or 84B.

19690-2 (multiple) rotating pistons and chambers and vice versa - gearboxes Rotating Piston

Figs. 90AB are showing a piston which is turning around in a chamber, within said chamber, which may be fixed, but always able to counter the torque derived by said piston. An enclosed space (channel) may be part of the axle, around which its centrum said piston is turning, just alike a piston moving on a crankshaft - based- on e.g. Figs. 11A (CT⁴), 11G (ESVT²), 111 (ESVT⁵). The centre of said axle may preferably be identical with the centre of said chamber, and the axis of the connecting rod may preferably be positioned perpendicular to the axis of the axis of the axle. A connecting rod between said piston and said axle may comprise the enclosed space of said piston, and this enclosed space may be communicating with the space within said piston and with said enclosed space in said axle. When e.g. a sphere shaped piston is being used, may the extension rod which is connecting said sphere with the channel in the axle, be constructed alike the rod shown in Figs. 14F and 14G, such that the length of the connecting rod may constantly adapting to the current distance between the centrum of said piston and the centrum of said axle (Figs. 90C,D). It depends on how the connecting rod is being connected to said axle, which pressure management technology may be used: CT and/or ESVT, or a third type. The CT demands a valve function, which means a sequential open/close connection between the channels in said connecting rod, and the channel in said axle. The ESVT demands an open connection between said channels.

The possibilities for the construction of the joint between the connecting rod and the axle depend additionally on how the torque is being transferred from the piston, through the connecting rod, to the axle, when the chamber may be fixed. Transferring the torque from the piston through the connecting rod to a rotating axle means that there is a fixed connection between said two construction elements. When an ESVT pressure management system is desired may the construction of said joint be relatively simple: a fixture (e.g. teeth (connecting rod) + corresponding grooves (axle)), and a channel through said fixture, which is constantly communicating with the channels in the connecting rod and the axle (Figs. ). When a CT pressure management system is desired, may the construction of said joint be more complex. This may be comprising a serial- and/or a parallel solutions of the fixture and the rotating channels, of which openings meet openings of fixed channels during a part of the rotation. The serial solution comprises a construction

⁴ Consumption Technology

21

⁵ Enclosed Space Technology where said fixture and said rotation are positioned on at least two different positions on said axle: thus, at least two joints. The parallel solution comprises a construction where said fixture and said rotation are combined in one joint.

For increasing the torque, more than one piston may be running in one chamber, there may be sub-chambers within said chamber, and when there is e.g. one piston per sub-chamber, each piston may preferably be positioned at the same circular position in each sub-chamber. This may be done to simplify the construction, so that the enclosed space of each connection rod per piston is communicating with the enclosed space of the axle. The pressure within each piston is than identical with that of the channel inside the other pistons.

Another possibility is that more than one piston-chamber combination are combined to an x-cylinder motor (x>l), where one or more pistons is/are turning in a chamber, said combination may turn around the same central axle (Fig. 92A), to which the torque of each piston is being transferred to enable the purpose of said motor to be performed: wheels, propeller, lifting etc.

Rotating Chamber

Fig. 91 A is showing a chamber, which is turning around a piston, the last mentioned may be fixed, but always able, to counter the torque derived from the chamber. The centre of said axle may preferably be identical with the centre of said chamber, and the axis of the connecting rod may preferably be positioned perpendicular to the axis of the axis of the axle. An enclosed space (channel) may be part of the axle, where around its centrum said chamber is turning, just alike the chambers in e.g.. Figs. 13A, (CT⁶); 12D,13E,F,G (ESVT); 14E (ESVT⁷).

A connecting rod between said piston and said axle may comprise an enclosed space, and this enclosed space is communicating with the space within said piston and said enclosed space in said axle (Figs. 91A,B).

When e.g. a sphere shaped piston is being used, may the connection rod which is connecting said sphere with the channel in the axle, be constructed alike the rod shown in Figs. 14F and 14G, such that the length of the connection rod may constantly adapting to the current distance between the centrum of said piston and the centrum of said axle (Figs. 90C,D). This construction may the identical with the construction of the combination where the piston is moving.

Consumption Technology

7 Enclosed Space Technology What has been said in the preceeding chapter about the construction of the joint of the connecting rod and the axle, when a piston is moving, is also applicable for the situation where a chamber is moving. In the situation where a chamber is moving may two main solution groups be possible: one, where the axle is fixed, and the chamber rotating around said axle, and where said chamber is transmitting the torque (Fig. 92A). The other group is when the axle is rotating, and it may be transmitting the torque derived by the chamber (Figs.92B,C; Figs. 93A,B).

In the case the axle is turning around said connecting rod (Fig.91AB), the ESVT may be used or the CT - it depends on the possibility to construct a valve between the enclosed space of the connecting rod, and the enclosed space of the axle: e.g. two valves may enable the CT (Fig. 91C, D), and no valve the ESVT (Fig.91E).

For increasing the torque, more than one piston may be present in one chamber, there may be sub-chambers within said chamber, and when there is one piston per sub-chamber, each piston may be positioned at ^"the same circular position in each sub-chamber, or may be at different circular positions as shown in e.g. Figs. 13A-G, 14A-H. The positioning at a same circular position may be done to simplify the construction, so that the enclosed space of each connection rod per piston is communicating with the enclosed space of the axle. The pressure within each piston is than identical with the pressure inside the other pistons.

When a chamber is turning, there are numerous possibilities to combine the several solutions for all the parameters.

When the chamber is rotating e.g. around a bearing mounted on an axle on a chassis of e.g. a vehicle, and the axle is turning around a bearing mounted on said chassis, and turning e.g. in the same direction, while the piston is fixed, e.g. on said chassis, the connecting rod may be fixed between said fixed piston, and said fixed axle. Said axle and said chamber may additionally be turning in the opposite direction. The channels in said connecting rod and axle of this combination of solutions may preferably be communicating with an ESVT system (Figs. 10M,13C).

When the chamber is turning e.g. around a bearing mounted on the chassis of e.g. a vehicle, and the axle is fixed, e.g. on said chassis, the piston may be fixed by a connecting rod which has been mounted fixedly on said axle, in order to obtain the necessary force moment to get said chamber rotate. The channels in said connecting rod and axle of this combination of solutions may preferably be communicating with an ESVT system (Figs. 91A-C). Figs. 91 G-I show a comparable solution, where the bearing of the chamber is mounted on the axle.

When there is more than one piston-chamber combination, where a chamber is turning, comprising one or more pistons, than a chamber of said combination may transfer the torque through e.g. a housing which is comprising at least one chamber, said housing may transferring the torque to e.g. a bearbox or an automatic gear(box), e.g. a Variomatic^®, to wheels, a propeller etc.

It may additionally be possible that each chamber of said combination is transferring its torque to an axle, around which said chambers are running (Fig. 93A,B). Said axle is rotating around a fixed axle, where the enclosed space of the fixed piston in the connecting rod, is communicating through a channel in said fixed axle with a pressure management system, preferably the ESVT system.

19690-2 - DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 90A shows one rotating piston 4000, positioned near a first longitudinal position in a circular chamber 4001, where the piston 4000 is connected to an axle 4002 by a connecting rod 4003, said axle 4002 and connecting rod 4003 are comprising each a channel 4004 and 4005, resp., communicating with each other. Said channel 4005 is the (first) enclosed space for the piston 4000. Said channel 4004 is the (second) enclosed space of said piston 4000. Said channel 4005 is communicating with the space within the wall of the piston 4000. The centre axises 3997 and 3998 are the horizontal and vertical, resp. centre axis of the chamber 4001. The centre point 3995 of said axises 3997 and 3998. Preferably is the axis (not shown as such) of said axle 4002 going through said centerpoint 3995, and is preferably positioned perpendicular the plane through the centre axis 3996 of said circular chamber 4001. The centre axis 4008 of the connecting rod 4003 is preferably going through said centre point 3995. The piston 4000' is shown at an ultimate first circular position of said chamber 4001, as well as at the second circular position of the piston 4000". The circular chamber 4001 is constructed over 360 degrees: from a second to a first longitudinal position. The piston 4000 is "turning clockwise in said chamber 4001 around the centre point 3995. The channel 4004 is communicating with a pressure management system, and that may be a CT- and/or an ESVT-system. The contra weigth 3994, which is positioned opposite the connecting rod 4003 in relation to the centre point 3995.

Fig. 90B shows a detail of the assembling of the connecting rod 4003 onto the axle 4002. This is done by having a hub 4009, which is in a longitudinal direction of the axle 4002 slidingly mounted on the axle 4002, where the teeth 4007 of said axle 4002 fit into the corresponding grooves 4007' of said hub 4009. This construction makes it possible to transfer a torque from the connecting rod

4003 to the axle 4002. This construction enables additionally a constant communication through the channel 4006 in said axle and the channel 4006' in the wall of said hub 4009 with channel (the first enclosed space) 4005 in said connecting rod 4003, and with the channel (the second enclosed space)

4004 in said axle 4002. The centre axis 4008 is the centre axis of the channels 4005, 4006 and 4006', resp., and is also the longitudinal centre axis of said connecting rod (4003). This centre axis 4008 is positioned perpendicular to the centre axis (not shown) of the axle 4002. The connection rod 4003 is mounted on said hub 4009. The connecting rod 4003 is shown having a central rod 4010, in which the enclosed space 4005 is situated, and reinforcement fins 4011, between which a bolt 4016 is situated for mounting the connection rod 4003 on said hub 4009. The washer 4012 and the spring washer 4013. The end 4017 of said central rod 4010 is positioned in a recess 4015 of said hub 4009. The sealing 4018 between said end 4017 and said recess 4015. The contra weight 3994 is shown as a part of said hub 4009.

Fig. 90C shows the extension rod 4020 of the connecting rod 4003 on which the piston 4000 is mounted. The piston 4000 is shown being positioned near a first circular position 4021. For the rest is the construction identical with the one shown in Fig. 14F. The connecting rod 4003 is comprising an extension rod 4020, which is moving with a sliding fit, sealingly by means of two O-rings 4021 and 4022, to and from the axle 4002, within end 4023 of the channel 4005 of connection rod 4003, so as to enable compensation for the changing distance of the wall 4024 of the piston 4000 to said axle 4002. Within said extension rod 4020 is a channel 4025, which is communicating with the space 4026 of said piston 4000 through a channel 4027, and the channel 4005 of the connecting rod 4003. The distance 1 between the end 3991 of the extension rod 4020 and the crossing point 3990' between the centre axis 3996 of the chamber 4001 and the centre axis 4008 of the connecting rod 4003.

Fig. 90D shows the extension rod 4020 of the connection rod 4003 on which the piston 4000" is mounted, and is shown, when the piston 4000 is positioned at a second circular position 4028. For the rest is the construction identical with the one shown in Fig. 14G, and Fig. 90C. The distance V between the end 3991 of the extension rod 4020 and the crossing point between the centre axis 3996 of the chamber 4001 and the centre axis 4008 of the connecting rod 4003. The length Γ < 1 (shown in Fig. 90C).

Fig. 90E shows the construction of Fig. 90A communicating with the CT - pressure management system based on Fig. 11A, now worked out in a plane through the centre axis 4029 of the axle 4002. The joint 4051 between the connecting rod 4003 and the axle 4002 of Fig. 90A,B is according Fig. 11D. The channel 4005 of the connecting rod 4002 is communicating with the channel 4004 of the axle 4002. The last mentioned channel 4004 is communicating with the channels 822 and 823, resp. Please see Fig. 11A and 11D for the description of further reference numbers of said drawings.

Fig. 90F shows the ESVT - pressure management system based on Fig. 11G, and a joint 4052 according to Fig. 1 IT, for the transition of the axle 4002, comprising the channel 4004, with the channel 4005 of the connecting rod 4002 of Figs. 90A,B. Please see Figs. 11G and 11T for the description of the further reference numbers of said drawings.

Fig. 90G shows the ESVT - pressure management system based on Fig. I ll, and a joint 4052 according to Fig. 1 IT for the axle 4002, comprising the channel 4004 and the connecting rod 4003 which is comprising the channel 4005, as shown in Figs. 90A,B. Please see Figs. I ll and 1 IT for further reference numbers of said drawings.

Fig. 90H shows the ESVT - pressure management system based on Fig. 90G, in combination of a camshaft 4060, which is controlling the timing of the ESVT system of Fig. I ll, while the energy comes from a combustion motor 4061, driven by H₂, derived from electrolyses of H₂0, according to Fig. HQ. Please see Figs. 90G, 111, 1 IT and HQ for the description of further reference numbers of said drawings, and for other details:—

Fig. 901 shows 4 rotating pistons 5070, 5071, 5072, 5073, resp. in a circular chamber 5074, which is comprising 4 sub-chambers 5075, 5076, 5077, 5078 - one for each piston - said circular chamber 5074 may preferably be fixed. Said rotating pistons 5070, 5071, 5072, 5073 are each positioned at the same circular position in each of the sub-chambers 5074, 5075, 5076, 5077 - the circulation of said pistons is shown as being clockwise around the centrepoint 5079 of said circular chamber 5074. Each piston 5070, 5071, 5072, 5073 is rotating around the same axle 5085, of which centre is identical with said centerpoint 5079. Each piston piston 5070, 5071, 5072, 5073 is connected to said axle 5085 by a connecting rod 5080, 5081, 5082, 5083, which is comprising an extension rod 5090, 5091, 5092, 5093, as described in Fig. 90C,D. In fact is this construction regarding said pistons 5070, 5071, 5072, 5073, connecting rods 5080, 5081, 5082, 5083 and extension rods 5090, 5091, 5092, 5093 4x the construction shown in Figs. 90A,B. All 4 connecting rods 5090, 5091, 5092, 5093 have been assembled by a bolt to a common hub 4029. Said hub 4029 is fixly mounted on said axle 5085 by teeth (4007) of said axle 5085, fitting into corresponding grooves (4007') of said hub 4029, as shown in Figs. 90B.

Fig. 90J shows an enlargement of the assembly of the connecting rods 5080, 5081, 5082, 5083 and the axle 5085 of Fig. 901. In fact is this joint a 4-double of the joint shown in Fig.

90B, in 4 equal circle segments over the 360 . The common hub 4053.

The channels 5086, 5087, 5088, 5089 of each connecting rod 5080, 5081, 5082, 5083 are communicating constantly with the channel 5090 within said axle 5085, and thus with each other. It enables a direct communication between the space (not shown here - please see Figs. 90C,D) within each piston 5070, 5071, 5072, 5073 and the channel 5090 within the axle 5085, thus this configuration functions preferably with an ESVT- pressure management system.

Fig. 90K shows the construction of Fig. 901, J which is communicating with an

ESVT-pressure management system according to Fig 111, and a further development of a new joint 4054: doubling: mirrored around the centre axle of said axle of the joint 4052 based on Fig. 1 IT, in combination with the common hub 4053 of Fig. 90J. Please see Fig. 11T for the description of the parts of said joint.

Fig. 90L shows a preferred embodiment of the motor, based on the construction of the joint 4054 shown in Fig. 90K in combination with a camshaft 4060, which is controlling the timing of the ESVT - system, while the energy comes from a combustion motor 4061, driven by ¾, derived from electrolyses of H₂0, on electrical energy from a battery 832, according to Fig. HQ. Please see Figs. 90K and 1 1Q for the description of further reference numbers of said drawings.

Fig. 91 A shows one circular chamber 4030 (over 360°) which is rotating anti- clockwise around an axle 4032, and is suspended by 3 spokes 4034. Said spokes 4034 are shown in a different cross-section than the cross section of the connecting rod 4033. A piston 4031 is positioned near a first circular position in said circular chamber 4030. Said piston 4031 is preferably fixed, by a connecting rod 4033, the suspension of the last mentioned, the hub 4038, is fixedly mounted on said axle 4032 by teeth and corresponding grooves (please see Fig. IB), which take the reaction forces from the circular chamber 4030 on the piston 4031. Between the hub 4035 of said spokes 4034 and said axle 4032 is a bearing 4039, which may be fixed onto the hub 4035 of said spokes 4034 by an appropriate fit, enabling the hub 4035 of said spokes 4034 to turn around said axle 4032. The belt 874, turning near the edge of the chamber housing 4036, is running according the direction of the rotation of said chamber 4030.

Fig. 91 B shows a detail of the assembling of the connecting rod 4033 and the axle

4032. The hub 4035 of the spokes 4034 is comprising the bearing 4039, which is with an appropriate fit turning together with the turning hub 4035 of the spokes 4034. No valve function is is arranged here, because the bearing 4039 is belonging to a different cross-section than the one comprising the channels 4044 annd 4045, of the wall of the axle 4032 and the wall of the upper part 4038-1 of the hub 4038, resp. The hub 4038 of the connecting rod 4033 is comprising of two parts: upper part 4038-1, which is connected to the connecting rod 4033, and the bottom part 4038-2. Said upper and bottom part are bolted together by bolt 4040, which additionally bolts the connection rod 4033 to the hub 4038. The spring washer 4041 and the washer 4042. The hub 4038 is comprising grooves 4007' fitting into theeth 4007. There is a constant communication possible between the channel 4043 of said axle 4032 to the inside of the piston 4031, through the channel 4044 of the wall of the axle 4032, channel 4045 through the wall of the upper part of the hub 4038-1 and the channel 4046 through the connecting rod 4034. The channel through the extension rod is not shown - please see Figs. 90C,D. Due to the constant communication, the use of an ESVT system is preferable, specifically when more than one chamber is applied on one axle, and the use of a CT system is optional.

All of the solutions for a combination with the CT - and/or ESVT pressure management which complied to the embodiments of Figs. 90A-D are also applicable for the embodiments of Figs. 91A,B.

Not shown, but only mentioned is a chamber,- with 4 sub-chambers, comprising 4 pistons, based on the configuration shown in Fig. 91A,B and alike Figs. 901, J. Said chamber is rotating around an axle, of which centre axis is going through the centrepoint of the centre line of said circular chambers. The space within each piston is constantly communicating through channels (enclosed spaces) in each of the 4 extension- and connecting rods with the channel in said axle, and this configuration is preferably functioning with the ESVT - system.

Fig- 91 C shows a with Fig. 91 B comparable construction, with the difference, that the bearing 5100 is both a part of the hub 5101, which is assembling the connecting rod 5102 to the axle 5103, and the hub 5104, which is connecting the spokes 5105 with its hub 5106 (please see Fig. 9 ID) with said axle 5103. And, the channel 5109 in the wall of the axle 5103 is now positioned in the part of the axle 5103, where the bearing 5100 is positioned.

The cross-section -L is the section through the hub 5101 of the connecting rod 5102 and the axle 5103, where the axle 5103 is fixly connected to the hub 5104 by teeth 5107 fitting in grooves 5108. The cross-section N-M is the section through the hub 5106 (please see Fig. 9 ID) of the spokes 5105 and the axle 5103, where the hub 5106 can turn around said axle 5103 by means of the bearing 5100.

Fig. 91D shows the cross-sections N-M and K-L of Fig. 90C. Additionally is shown a cross-section of the chamber 5110, and the wall 5111 of said chamber 5110 is comprising the opening 5112 for the extension rod (not shown here - please see Fig. 90CJD) and a bigger opening 5113 for the connecting rod 5102.

The fit of the bearing 5100 with the hub 5101 of the connecting rod 5102 is such that the bearing 5100 can turn in the hub 5100 of the connecting rod 5102, while turning cannot be done within the hub 5106 of the spokes 5105. The fit of said bearing 5100 with the axle 5103 is such, that the bearing can turn around said axle 5102. The result is that the channel 5109 is not having a constant communication with the channel 51 14 of said axle 5103, when the chamber 5110 is rotating around said axle 5103 - the CT pressure management system can be used here. Together with the embodiments shown in Figs. 91A-D (incl.) are the preferred embodiments of the rest of the motor, earlier shown in Fig. 90E (CT), Figs. 90F-H (incl.) (ESVT).

Fig. 91E shows the connection of the channel 4035 of the connection rod and the channel 4034 of the axle 4032, where a constant communication is possible between said channels 4035 and 4034. The bearing 4039 is rotating together with the connection rod 4033, with the same rotating speed, so that the channel 4037 is always communicating with the channel 4035 of the- connection rod 4033. The central axis 4036 of the connection rod 4033. The axle 4040 is comprising an addtional channel 4041. Said channel 4041 is constantly communicating with the channel 4032 of said axle 4040, through channel 4042. Said channel 4041 is additionally constantly communicating with the channel 4037 of the bearing 4039, through channel 4045 of the upper hub 4038-1. The part 4046 of the axle 4040 has a reduced diameter, approximately around the channel 4042 in the wall of said part 4046. . The channel 4035 of the connection rod 4035 is constantly communicating with the piston 4031 , according Figs. 90C and 90D (where a sphere type piston is used). The channel 4034 in the axle 4032 is communicating with a pressure management system.

The ESVT⁸ may be working fine with this construction.

For the valves to be used in the joint of the axle and the connection rod: when using the CT²: please see Fig. 11D and derived therefrom e.g. shown in Fig. 90E (ref. 4051). For the ESVT¹ please see Fig.1 IT, and derived therefrom e.g. shown in Fig. 90F (ref. 4052) and Fig. 90K (ref. 4054).

The fit between the bearing 4039 and the upper hub 4038-1 and lower hub 4038-2 may be such that the bearing is not movable relative to the hub parts 4038-1 and 4038-2. Which is why the channel 4037 in the wall of the bearing 4038-1 is always communicating with the channel 4045 in the wall of the upper hub 4038-1, and thus will there be a constant communication between the channel 4032 of the axle and the channel 4035 of the connecting rod 4033. The use of the ESVT system may be possible.

If the bearing 4039 would have a sliding fit with said hub 4038-1 / 4038-2 and e.g. a squeezing fit with the axle 4040, said communication will be interrupted when the hub 4038 is rotating around said axle. The use of the CT system may be possible

⁸ Enclosed Space Volume Technology

2 Consumption Technology Fig. 92A shows schematically a 3-cylinder motor 4090, where the pistons 4091 are moving in circular chambers 4092, which are identical, and which have been positioned parallel to each other, around a main motor axle 4094, with a central axis 5000 - said chambers 4092 are interconnected by a housing 4095, and a gearbox 4093 is mounted on said assembly by a bolt 4096, spring 4097 and washer 4098. The main motor axle 4094 of the motor 4090 is communicating directly with the axle 5004 of the gearbox 4093. said gearbox 4093 is comprising a driveshaft axle 5000. In said gearbox 4093 is a reverse incorporated. Not shown,- but as an -alternative may there be inserted a clutch in between the main motor axle 4094 and the axle 5004, where the main motor axle 4094 is communicating through said clutch with the axle 5004 of said gearbox 4093, when the clutch is pressed on a wheel (not shown), e.g. a flywheel, which is constantly communicating with the main motor axle 4094. When the clutch is not pressed on said flywheel, is the motor 4090 turning free of the axle 5004 of the gearbox 4093, and by that free of the outgoing axle 4099 of said gearbox 4093.The pressure management system 5001, preferably a ESVT system, which is communicating with the channel 5002, which is communicating with the enclosed space 5003 of each piston 4091, and the inside 5006 of each piston The bolts 5004 (with spring and washer) are mounting the two chamber parts 4092-1 and 4092-2 together for each chamber 4092. The pistons 4091 are transferring their torque by a hub 5005 to the main motor axle 4094, e.g. according to Figs. 90A-C or according to Figs. 90I,J.

Fig. 92B shows schematically a 3-cylinder motor 5010, where a piston 5011 is moving in a circular chamber 5012. Said chambers 5012 are identical, and positioned parallel to each other, around the main motor axle 5013. A housing plate 5017, which is keeping the chambers 5012 together. The torque generated by the pistons 5011 are being transferred through a connecting rod (50xx) by the hubs 5019 to the main motor axle 5013, e.g. according to Figs. Figs. 90A-C or according Figs. 90I,J, or according to Figs. 91A-D. On each side on said main motor axle 5013 is a variable pitching wheel 5014 assembled, which are connected by a belt 5021 to comparable wheels 5015 on a wheel axle 5016 of a vehicle; shown is the high pitch at the side of the motor 5010, and a low pitch at the side of the wheel axle 5016 (vehicle is moving quickly) The distance x shows that this distance remains unchanged, when the pitch of the wheels 5014 and 5015 change - said change may be any pitch in between said high and low pitch. The channel 5019 in the centre of the main motor is directly communicating with the pressure management system 5020, preferably an ESVT- system. Not shown is the reverse arrangement, so that the vehicle can move backwards as well as forwards. Fig. 92C shows the same as Fig. 92B, but where the pitch of the wheel 5014' at the side of the motor 5010 is small, and a high pitch of the wheel 5015' at the side of the wheel axle 5016 .(vehicle is moving slowly). Fig. 93A shows schematically a 3-cylinder motor 5020 where the chambers 5021 are rotating around a central axle 5022. Said chambers 5021 are each connected to a central axle 5022 by corner brackets 5023, 5023' on each side of a chamber 5021, so that the torque generated by a chamber 5021 is being transferred through said corner bracketes to said central axle 5022, because said central axle 5022 is comprising parts 5022' outside each hub 5034 of each piston 5025, which are only connected to each other by said brackeyts 5023, 5023', and further comprising a bearing (5033), which is comprising parts (5033'), corresponding to the parts of said central axis (5022) The hubs 5034 are mounted on the inner axle 5032. Said central axle 5022 is communicating with an external gearbox 5024, through a gear wheel 5028. Said gear wheel is communicating with a gear wheel 5029. Said gear wheel 5029 is indirectly communicating with the driveshaft axle 5030. The rotation direction 5031 of drive shaft axle 5030. Each chamber 5021 is comprising a piston 5025, and a ring 5026, which functions as a flywheel, and which is positioned farthest from the central axis 5022. Said pistons 5025 are assembled to the inner axle 5032 by a hub 5034. Said inner axle 5032 is mounted by a fixture 5035, 5035' to the vehicle and gearbox, respectively.. Between the inner axle 5032 and the axle 5022 is a bearing 5033 (please see the enlargment). The pressure management system 5027, preferably the ESVT - system. The communication 5036 of the pressure management system 5027 with the channel 5037 in said inner axle 5032. Said channel 5037 is communication with the channel 5039 in the connecting rod 5040 (schematically shown), which is communicating with the space 5038 within the piston 5025. Fig 93B shows an enlargement (4:1) of the left corner of the central axis 5022, and the bearing 5033 between the central axle 5022 and the inner axle 5032. The fixture 5035.

207 DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 100 shows the so-called indicator diagram. This diagram schematically shows the adiabatic relation between the pressure p and the pump stroke volume V of a traditional single-stage oneway working piston pump with a cylinder with a fixed diameter. The increase in the operating force to be applied per stroke can be read directly from the diagram and is quadratic to the diameter of the cylinder. The pressure p, and thus the operating force F, increases during the stroke normally until the valve of the body to be inflated has been opened.

Fig. 102A shows the indicator diagram of a piston pump according the invention. It shows that the diagram for pressure p is similar to that of traditional pumps, but that the operating force is different and depends entirely on the chosen area of the transversal cross-section of the pressurizing chamber. This depends entirely on the specification, e.g. that the operating force should not exceed a certain maximum or that the size of the operating force is fluctuating according to ergonomic demands. This is specifically demanded in the case when a manually operated pump is only transporting the media without significant change in the pressure as it is e.g. the case with water pumps. The shape of the longitudinal and/or transversal cross-section of the pressurizing chamber may be any kind of curve and/or line. It is also possible that the transversal cross-section e.g. increases by increasing pressure (Fig. 102B). An example of the operating force is the dashed thick line, 1 or 2. The different wall possibilities marked 1 and 2 correspond to the earlier mentioned lines 1,2 of the diagram. The A-section relates to a pump of which only the piston is moving, while the B-section relates to pumps where only the chamber is moving. A combination of both movements at the same time is also possible.

Fig. 102B shows an example of an indicator diagram of a piston pump that has a chamber with a transversal cross-section that increases by increasing pressure.

Figs. 103A,B,C,D show details of the first embodiment. The piston moves in the pressu- rizing chamber which comprises cylindrical and cone-shaped portions with circular transversal cross-sections with diameters that decrease when the pressure of the gaseous and/or liquid media increases. This is based on the specification that the operating force should not exceed a certain maximum. The transition between the various diameters is gradual without discrete steps. This means that the piston can slide easily in the chamber and adapt itself to the changing areas and/or shapes of the transversal cross-sections without loss of sealing ability. If the operating force has to be lowered by increasing pressure, the transversal cross-sectional area of the piston is decreasing and by that the length of the circumference as well. The circumferical length reduction is based on compression up to the buckling level or by relaxation. The longitudinal cross-section of the piston means is trapezoid with variable angle a less than e.g. 40° with the wall of the pressurizing chamber, so that it cannot deflect backwards. The dimensions of the sealing means change in three dimensions during every stroke. A supporting portion of the piston means, e.g. a disk or integrated ribs in the sealing means, e.g. positioned on the non-pressurized side during a pumping stroke of the piston protects against deflection under pressure. A loading portion of the piston means, e.g. a spring washer with several segments, may also be mounted e.g. on the pressurized side of the piston. This squeezes the flexible sealing portion towards the wall. This is expedient if the pump has not been used for some time and the piston means has been folded for some time. By moving the piston rod, the sides of the trapezoid cross-section of the sealing portion of the piston means will be pushed axially and radially, so that the sealing edge of the piston follows the decreasing diameter of the pressurizing chamber. At the end of the stroke, the bottom of the chamber in the centre has become higher in order to reduce the volume of the dead room. The piston rod may mainly be guided in the cap which locks the pressurizing chamber. As the piston in both directions of its movement seals to the wall of the chamber, the piston rod e.g. comprises an inlet channel with a spring force-operated valve, which is closed in case of overpressure in the chamber. Without the use of the loading portion in the piston means, this separate valve may be superfluous. In the pump design according to the invention, the parts of the pump have been optimized for working forces. The inside diameter of the pump is over the main part of the pump chamber length larger than that of existing pumps. Consequently, the inlet volume is higher, even though the volume of the remaining part of the chamber is lower than that of existing pumps. This ensures that the pump can pump quicker than existing pumps, while the maximum operating force required is significantly reduced and lower than the level reported by consumers to be comfortable. The length of the chamber can be reduced, so that the pump becomes practical, even for women and teenagers. The volume of a stroke is still higher than that of existing pumps.

Fig. 103 A shows a piston pump with a pressurizing chamber 1 with portions of different areas of its transversal cross-sections of wall sections 2,3,4 and 5. The piston rod 6. The cap 7 stops the piston means and guides the piston rod 6. The transitions 16,17 and 18 between the section with the walls 2,3,4 and 5. The longitudinal centre axis 19 of the chamber 1. The piston 20 at the beginning and 20' at the end of the pump stroke.

Fig. 103B shows the sealing portion 8 made of an elastic material and the loading portion 9, e.g. a spring washer with segments 9.1, 9.2 and 9.3 (other segments not shown) and a support portion 10 of the piston means attached to the piston rod 6 between two portions of locking means 11. The piston rod 6 has an inlet 12 and a valve 13. The angle a between the sealing portion 8 of the piston means and the wall 2 of the pressurizing chamber 1. The sealing edge- 37. The distance a is the distance from the sealing edge 37 to the central axis of the chamber 1 in a transversal cross-section at the beginning of the stroke.

Fig. 103C shows outlet channel 14 in a means 15 which reduces the volume of the dead room. Angle a₂ between the sealing portion 8' of the piston means and the wall 5 of the pressurizing chamber 1. The distance a' is the distance from the sealing edge 37 to the central axis of the chamber 1 in a transversal cross-section at the end of the stroke. Shown is that distance a¹ is approximately 41% of distance a. The loading portion 9'.

Fig. 103D shows the longitudinal cross-section of the chamber of a floor pump ( inside 60 - 19.3 mm, length 500 mm) according to the invention of which the transversal cross-sections are chosen so that the operating force remains approximately constant and is chosen in accordance with ergonomic demands: e.g. as in the Figure: 277 N. Other force sizes can also be chosen. This is only giving the starting point for the quantification of a floorpump according to the invention as a constant operating force may not be ergonomically correct. As a comparison the cross-sections of an existing low pressure floor pump (0j_nSide 32 mm, length 470 mm) is shown in dotted lines, and that of an existing high pressure floor pump ( ^de 27 mm, length 550 mm) is shown in dashed lines. It is clearly shown that the floor pump according to the invention both has a bigger stroke volume, thus faster inflating tyres, and a lower operating force than existing pumps. The chamber according to the invention can be tailored to ergonomic demands during the entire stroke.

Figs. 104A,B,C,D,E,F show details of the second preferred embodiment. The sealing portion of the piston means is made of an elastically deformable material supported by a support means which can rotate around an axis parallel to the center axis of the chamber. The consequence of this movement is that it supports a larger area of the sealing means the higher the pressure is in the chamber. The loading portion for the support portion initiates the movement of the support means. The loading portion in the form of a flat-shaped spring can change dimensions in a direction perpendicular to the centre line of the chamber. The spring becomes more and more stiff the higher the pressure in the chamber. It can also be a spring on the axis where the support means turns around. By decreasing the diameter of the sealing portion it increases its length. This is the case with an elastically deformable material which is only a bit compressable, like e.g. rubber. Therefore the piston rod sticks out of this sealing means at the beginning of a stroke. If other material for the sealing portion is chosen, its length may remain unchangend or may decrease by decreasing its diameter.

Fig. 104A shows a piston pump with a pressurizing chamber 21 with portions of different transversal cross-section areas. The chamber has cooling ribs 22 at the high-pressure side. The chamber can be (injection) moulded. The piston rod 23. The cap 24 guides the said piston rod. The piston 36 at the beginning and 36' at the end of a pump stroke.

Fig. 104B shows the elastically deformable sealing portion 25 which is fastened to the piston rod 23 by means 26 (not drawn). A part 27 of the piston rod 23 is sticking out of the sealing portion 25. Support portion 28 is hanged up on ring 29 which is fastened to the piston rod 23. Support portion 28 can turn around axis 30. Loading portion 31 comprises a spring which is fastened in a hole 32 onto the piston rod 23. The sealing edge 38.

Fig. 104C shows that part 27 of piston rod 23 is almost covered by the elastically deformed sealing means 25', which has now increased its length and decreased its diameter. The sealing edge 38'. The distance a' between the sealing edge 38 and the central axis 19 of the chamber is approximately 40% of that of distance a in the shown transversal cross-section.

Fig. 104D shows section A- A of Fig. 104B. The loading portion 31 is fastened at one end in the hole 32 of the piston rod 23. The support portion 28 and the ring 29. The support portion is stopped by a stop surface 33 (not drawn). The support portion 28 is guided by the guiding means 34 (not drawn).

Fig. 104E shows section B-B of Fig. 104C. The support means 28 and the loading means 31 are moved towards the piston rod 23. The rib 22. Fig. 104F shows an alternative for the loading means 31. It comprises springs 35 on each axis

30.

Figs. 105A,B,C,D,E,F,G,H show details of the third embodiment. It is a variant of the first embodiment. The sealing portion comprises a flexible impervious membrane for gaseous and/or liquid media. This material can change its dimensions in three directions without folds. This sealing portion is mounted in an O-ring which seals to the wall of the chamber. The O-ring is loaded to the wall by a loading means, e.g. a spring in the circumference. The O-ring and spring are further supported by a support means which can rotate around an axle fastened to the piston rod. This support means can be loaded by a spring.

Fig. 105 A shows a longitudinal cross-section of a piston pump analog to that of Fig. 103 A. The piston 49 at the beginning and 49' at the end of the pump stroke.

Fig. 105B shows a piston means at the beginning of a stroke comprising a sealing means 40: e.g. a stressed skin, that is fastened to a sealing means 41: e.g. an O-ring. This O-ring is loaded by a spring 42 which is positioned on the circumference of the sealing means 41 and sealing means 40. The central axis 39 of the spring 42. The O-ring 41 and/or spring 42 is supported by support means 43 that can rotate on axis 44 which is attached to the piston rod 45

and positioned perpendicular to the central axis 19. It comprises a certain amount of separate members 43', loaded in compression during the (compression) pump stroke. These are positioned around the circumference of the sealing means 40,41 and the loading means 42, which they support. The support means 43 can be loaded by a spring 46. The angle βι between the wall of the chamber 2 and the support means 43. The piston rod 45 is without an inlet or a valve. A supporting ring and/or loading ring in the form of a spring can be mounted in the O-ring as an alternative for spring 42 (not drawn). The sealing edge 48.

Fig. 105C shows the piston means at the end of the stroke. The sealing means 40', 4Γ is thicker than at the beginning of a stroke: 40,41. The spring 46'. The Angle β₂ between the wall 5 and the support means 43 at the end of a stroke. The distance a' between the sealing edge 48 and the central axis 19 of the chamber is approximately 22% of the distance a at the beginning of the stroke in the shown cross-section. Smaller distances e.g. 15%», 10% or 5% are possible, and depend only on the construction of the suspension of the piston on the piston rod. Therefore, this is also valid for all other embodiments. Fig. 105D shows section C-C of Fig. 105 A with support means 43, axle 44 and bracket 47. Fig. 105E shows section D-D from Fig. 105 A.

Fig. 105F shows the two positions of the piston 118 of Fig. 105G and 118' of Fig. 105H in a chamber.

Fig. 105G shows a piston which is made of a composite of materials. It comprises a skin 110 of elastic impervious material and fibers 111. The fiber architecture results in the dome-form when it is under internal pressure. This form stabilizes the piston- movement. As an alternative the sealing means may comprise a liner, fibers and a cover (not drawn). If the liner is not tight, an impervious skin may be added (not drawn). All materials at the compressed side of the piston comply with the specific environ mental demands of the chamber. The skin is mounted in a sealing portion 112. Within the skin and the sealing portion a spring-force ring 113 may be mounted and which can elastically deform in its plane, and which enhances the loading of the ring 114. The sealing edge 117.

Fig. 105H shows the piston of Fig. 105G at the end of a pump stroke. The dome has been compressed into shape 115, if there is still full overpressure. Shape 110' is a result if the overpressure is decreased e.g. after the media has been released.

Figs. 106A,B,C show details of the fourth embodiment. The piston means comprises a rubber tube which has a reinforcement, e.g. in the form of a textile yarn or cord wound around. The neutral angle between the tangent of the reinforcement winding and the centre fine of the hose (= so-called braid angle) is mathematically calculated to be 54°44'. A hose under internal pressure will not change dimensions 0ength, diameter), assuming no elongation of the reinforcement. In this embodiment, the diameter of the piston means decreases in relation to the decreasing diameter of the cross-section of the chamber at increasing pressures. The braid angle should be wider than neutral. The shape of the main part of the longitudinal cross-section of the pressurizing chamber is approximately a cone shape due to the behaviour of the piston means. At the end of the pump stroke, when the compressed medium has been removed from the chamber, the piston means increases its diameter and its length is decreased. The diameter increase is no practical problem. The sealing force from the piston to the wall of the pressurizing chamber ought to increase by increasing pressure. This may e.g. be done by the choice of a braid angle so that the piston diameter decreases a bit less than the decrease in diameter of the transversal cross-section of the chamber. Therefore, the braid angle may also be chosen to be smaller than neutral and/or being neutral. In general, the choice of the braid angle depends entirely on the design specification, and therefore the braid angle may be wider and/or smaller and/or neutral. It is even possible that the braid angle changes from place to place in the piston. Another possibility is that in the same cross-section of the piston several reinforcement layers are present with identical and/or different braid angles. Any type of reinforcement material and/or reinforcement pattern can be used. The place of the reinforcement layer(s) may be anywhere in the longitudinal cross-section of the piston. The amount of linings and/or covers may be more than one. It is also possible that a cover is absent. The pisto means may also comprise loading and supporting means, e.g. those showed earlier. In order to be able to adapt to larger changes in the areas of cross-sections of the chamber a bit different construction of the piston means is necessary. The cone comprises now fibers which are under tension. These are coiled together in the top of the cone near the piston rod, and at the open side of the cone at the bottom of the piston rod. These may also be fastened to the piston rod itself. The pattern of the fibers is designed e.g. so that these are under higher tension the higher the pressure is in the chamber of pump where the media is to be compressed. Other patterns are of course possible, just depending on the specification. They deform the skin of the cone,^" so that it adapt itself to the cross-section of the chamber. The fibers may lie loose on the liner or loose in channels between a liner and a cover or they may be integrated on one of the two or in both. It is necessary to have a loading means in order to obtain an appropriate sealing to the wall if there is no pressure under the cone yet. The loading member e.g. a spring force member in the form of a ring, a plate etc. may be build in the skin e.g. by inserting in a moulding process. The suspension of the cone on the piston rod is better than of the foregoing embodiments because the piston will now be loaded by tension. Therefore being more in balance and less material is needed. The skin and the cover of the piston may be made of elastically deformable material which comply with the specific environmental conditions, while the fibers may be elastically or stiff, made of an appropriate material.

Fig. 106A shows a longitudinal cross-section of a pump with chamber 60. The wall portions 61,62,63,64,65 are both cylindrical 61,65 and cone-shaped 62,63,64. Transitions 66,67,68,69 between the said portions. The piston 59 at the beginning and 59' at the end of a pump stroke.

Fig. 106B shows piston means 50, a hose with a reinforcement 51. The hose is fastened to the piston rod 6 by clamp 52 or similar. The piston 6 has ribs 56 and 57. Ribs 56 prevent the movement of the piston means 50 relative to the piston rod 6 towards the cap 7, while ribs 57 prevent the movement of the piston means 50 relative to the piston rod 6 away from the cap 7. Other configurations of the fitting may be possible (not shown). On the outside of the hose, a protrusion 53 seals against the wall 61 of the chamber 60. Besides the reinforcement 51 the hose comprises lining 55. As an example cover 54 is shown too. The shape of the longitudinal cross-section of the piston means is an example. The sealing edge 58.

Fig. 106C shows the piston means at the end of the stroke, where the gaseous and/or liquid medium is under pressure. The piston means may be designed in such a way that the diameter change only takes place via a radial change (not shown).

Fig. 106D shows the piston 189 of Fig. 106E and 189' of Fig. 106F at the begirining and at the end respectively of a pump stroke in a chamber of Fig. 106A.

Fig. 106E shows a piston means which has approximately the general shape of a cone with top angle 2ε_\. It is shown when there is no overpressure at the side of the chamber. It is mounted in its top on a piston rod 180. The cone is open at the pressurized side of the piston. The cover 181 comprises a sealing portion shown as a protrusion 182 with a sealing edge 188 and an inserted spring force member 183, fibers 184 as support means and a liner 185. The member 183 provides a loading to the cover, so that said protrusion 182 seals the wall of the chamber if there is no overpressure at the side of the chamber. The fibers 184 can lie in channels 186, and these are shown situated between the cover 181 and the liner 185. The liner 185 can be impervious - if not, a separate layer 209 (not shown) at the pressurized side is mounted on the liner 185. The fibers are mounted in the top 187 of the cone to the piston rod 180 and/or to each other. The same is the case at the bottom end of the piston rod 180.

Fig. 106F shows the piston means at the end of a stroke. The top angle is now 2ε₂ and the distance a' between the sealing edge 188 and the central axis 19 of the chamber is now approximately 44% of that distance a at the beginning of the stroke in the shown cross-section.

Fig. 107A,B,C,D,E show details of the fifth embodiment of the pump, with a piston which is constructed as another composite structure, comprising a basic material which is very elastic in all three dimensions, with a very high degree of relaxation. If it is not tight of itself, it may be made tight with e.g. a flexable membrane on the pressurized side of the piston means. The axial stiffness is accomplished by several integrated stiffeners, which in a transversal cross-section lie in a pattern, which optimally fills this section, while the in-between distance is reduced the smaller the diameter of the transversal cross-sectional section is, which in most cases means the higher the pressure in the pressurizing chamber is. In the longitudinal section of the piston the stiffeners lie in several angles between an axial direction and the direction of the surface of the piston means. The higher the pressure rates are, the more these angles are reduced and come near the axial direction. Now therefore the forces are being transferred to the support means, e.g. a washer, which is connected to the piston rod. The piston means can be mass-produced and is inexpensive. The stiffeners and, if necessary, the sealing means in the form of said flexible membrane, may be injection moulded together with said basic material in one operation. E.g. may the stiffeners be bonded together in the top, which makes handling easier. It is also possible to make the membrane by 'burning' it in said basic material, during or after injection moulding. This is specifically convenient if the basic material is a thermoplast. The hinges should than not be 'burned'.

Figs. 107F,G,H,I,J,K,L,M shows embodiments of the chamber and a sixth embodiment of the piston, fitting to this chamber. The sixth embodiment of the piston is a variant on the one of Fig. 107A,B,C,D,E. If the change^" of the area of a transversal cross-section of the piston and/or the chamber between two positions in the direction of movement is continuous but still so big that this results in leakages, it is advantageous to minimize the change of the other parameters of the cross-section. This can be illustrated by using e.g. a circular cross-section (fixed shape): the circumference of a circle is D, while the area of a circle is ¼ π D² (D = diameter of the circle). That is to say, a reduction of D will only give a linear reduction of the circumference and a quadratic reduction of the area. It is even possible to also maintain the circumference and only reduce the area. If also the shape is fixed e.g. of a circle there is a certain n inimum area. Advanced numeric calculations where the shape is a parameter can be made by using the below mentioned Fourier Series expansions. 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:

f ( x ) ^{~ +}∑c_P∞ ^χ) +∑d_P sin (px) where

2

dp =— \l f (x) ssn x) dx

71

0 < χ≤2π, x e N P≥0 , p e '//

Cp = cos-weighted average values off(x),

d_p = sin-weighted average values of f(x),

p = representing the order of trigonometrical fineness

Figs. 107F, 107K 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. As an example: Figs. 107L, 107M show 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 miriirnized. By using a starting area, and a starting boundary- length it is possible to count on a smallest possible curvature for a certain desired target area.

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 107F, 107K, 107L, 107M 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). One characteristic of these curves is that when a line is drawn from the mathematical pole which lies in the section plane it will intersect the curve at least one time. The curves are symmetrical towards a line in the section plane, and could also have been generated by the single Fourier Series expansion which follow. A piston or chamber will be more easy to produce when the curve of the transversal cross-section is symmetric with reference to a line which lies in the section plane through the mathematical pole. Such regular curves can approximately be defined by a single Fourier Series expansion: f ( * ) ^{= £}; ⁺∑c_P∞s (px)

p-l

where

0≤χ≤2π, x e fj P≥0 , p e

C_p = weighted average values of f(x),

p = representing the order of trigonometrical fineness.

When a line is drawn from the mathematical pole it will always intersect the curve only one time. Specific formed sectors of the cross-section of the chamber and/or the piston can approximately be defined by the following formula: f ( x ) = ~ ⁺∑c_P cos (3px) i₅

* p-l

Where

Cp =— f (^χ)∞s(3px) dx

71 p≥0 , p e

c_p = weighted average values off(x),

p = representing the order of trigonometrical fineness

and where this cross-section in polar co-ordinates approximately is represented by the following formula: r = ro + a. sin f- φ)

where

ro≥ ,

a≥0,

m≥ 0, m e R,

n≥ 0, n e R,

0 < φ < 2π, and where

r the limit of the "petals" in the circular cross section of the activating pin, ro the radius of the circular cross section around the axis of the activating pin, a the scale factor for the length of the "petals",

max r₀ + a

m the parameter for definition of the "petal" width

n the parameter for definition of the number of "petals" φ = the angle which bounds the curve.

The inlet is placed close to the end of the stroke due to the nature of the sealing portion of the piston means.

These specific chambers may be produced by injection moulding, and e.g. also by the use of so-called superplastic forming methods, where aluminium sheets are heated and pressed by air pressure either forced in a tool cavity or formed using also tool movement.

Fig. 107A shows a piston pump with a pressurizing chamber 70 in a longitudinal section with a cylindrical portion 71, a transition 72 to a continuous concave curved portion 73, another transition 74 to an almost cylindrical portion 75. The piston means 76 and 76' is shown at the beginning respectively at the end of the pump stroke. At the end of the outlet channel 77 a check valve 78 can be mounted (not shown).

Fig. 107B shows the piston means 76 comprising an elastic material 79 which gives the longitudinal section of the piston at low pressures the form of approximately a cone. The material 79 functions also as a loading means. The bottom comprises a sealing means 80, which can be folded radially - this sealing means 80 is partially also working as a loading means. The main support means comprises of stiffeners 81 and 82, of which the stiffeners 81 mainly support the sealing edge 83 of the piston means to the wall of the pressurizing chamber 70 while the other stiffeners 82 transfer the load from the sealing means 80 and the basic material 79 to the support means 84 e.g. a washer which is itself supported by the piston rod 6. The sealing means 80 is in this position of the piston means 76 still a little bit folded, so that fold 85 will load the sealing edge 83 the more the higher the pressure will be in the chamber 70. Stiffeners 82 are joined together in the top by joint 86. In this position of the piston means 70 the stiffeners 81 and 82 having angles between γ and δ with the central axis 19, where δ is approximately parallel with the central axis 19 of the pressurizing chamber 70. The angle c i between the surface of the piston 76 and the central axis 19.

Fig. 07C shows the piston means 76' at the end of the pump stroke. The sealing means 80 has been folded together, while the elastic material 79 has been squeezed together, resulting in the stiffeners 81,82 are directed approximately parallel with the central axis 19. The angle φ₂ between the surface of the piston means 76' and the central axis 19 is positive, but almost zero. The distance a' between the sealing edge 83 and the central axis 19 in the shown cross-section is 39% of that distance a at the beginning of the stroke. The sealing means 80'.

Fig. 107D shows a transversal cross-section E-E of the piston means 76, showing the basic elastic material 79, stiffeners 81 and 82, folds 87 of the sealing means 80. Piston rod 6.

Fig. 107E shows a transversal cross-section F-F of the piston means 76', showing the basic elastic material 79, stiffeners 81 and 82, folds 87 of the sealing means 80. Clearly shown is that the elastic material 79 is squeezed together.

Fig. 107F 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 parameterization 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. 107G 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 piston 163. The chamber has portions of different cross-sectional area's of its transversal cross- section of wall sections 155,156,157,158. The transitions 159,160,161 between said wall sections. Shown are cross-sections G-G, H-H and I-I. Cross-section G-G has a circleround cross-section, while cross-section H-H 152 has approximately an area between 90-70% of the one of cross-section G-G.

Fig. 107H shows transversal cross-section H-H 152 of Fig. 107G 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. 1071 shows a transversal cross-section I-I of Fig. 107G 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. Also shown is the smallest part of the chamber. Fig. 107J shows a variant of the piston of Fig. 107A-C in cross-section H-H from Fig. 107G. The piston is now made of elastic material which is also impervious so that a separate sealing means is not necessary. The distance c and d are different and by that the deformations of the piston in the same transversal cross-section H-H.

Fig. 107K 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 parameterization 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, but it is also possible to increase these areas by remaining the circumference constant. 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 size of the cross-sectional area bottom right is approximately 49% of the starting area size

left, top.

Fig. 107L 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. 107L is: The length specified by_y is determined by: where As an example from Fig. 103D: Domain area A₀ = π(30)² and boundary length L = 60π = 188.5 corresponding to the area and boundary length of a disk of radius 30. The length is required to be constant, but the area is decreased to the value Ai to be specified. The desired final configuration should have the area Ai = π (19/2)² = 283.5. The convex curve with the smallest possible curvature of the boundary curve is now:

r = 1.54

K = l/r = 0.65

x = 89.4

The curve on the Figure is not on scale and the Figure shows only the principle.

The curve may further be optimized by exchanging the straight lines by curves which may improve the sealing of the piston to the wall.

Fig. 107M shows a non-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. 107L is:

π + 4

The length specified by x is determined by:

χ = -Σ - ( 1 + π )

2 π + 4 where

r - smallest radius of curvature

L = boundary-length = constant

A i - decreased value of the starting domain area AQ

The non-convex curve (with obvious modifications of the string-like intermediate double curve) with the smallest possible curvature of the boundary curve: r = 6.3

K = 1/r = 0.16

x = 42

Fig. 108A,B,C show a seventh embodiment of the pump, with a piston means which is constructed as another composite structure, comprising a compressible medium as e.g. a gaseous medium like for example air (also is possible: only a non-compressible medium as e.g. a liquid medium like water or a combination of compressible and a non-compressible medium) within a closed chamber which is constructed as e.g. a reinforced hose. It may be possible that the lining, reinforcement and cover at the pressurized side of the piston means is different from that of the non-pressurized side - here the skin can be built up as a pre-formed shaped skin, holding this shape during the pump stroke. It is also possible that the skin is made of two or more parts, which itself are pre-formed shaped, one at the non-pressurized side of the piston means, the other on the pressurized side (please see Fig. 108B part X resp. parts Y+Z). During the pump stroke the two parts hinge in each other (please see Fig. 108B XY and ZZ). The adaptation of the sealing edge to the chamber in the transversal cross-section may result in a change of the cross-section of the piston at its sealing edge, and this may result in a change of the volume inside the piston. This volume change may give a change in the pressure of the compressible medium and may result in a changed sealing force. Moreover, the compressible medium functions as a support portion as it transfers the load on the piston to the piston rod.

Fig. 108 A shows a longitudinal section of the pressurizing chamber 90, comprising a continuous convex curve 91, with the piston 92 at the beginning of the pump stroke, and 92' at the end hereof. The high pressure part of the chamber 90 comprises an outlet channel 93 and an inlet channel 94 both with a check valve 95 and 96, respectively (not shown). For low pressure purposes the check valve 95 can be removed.

Fig. 108B shows piston 92 which is vulcanised directly on the piston rod 97, comprising a compressible medium 103 within a lining 99, a reinforcement 100 and a cover 101. Part X of the skin 99,100,101 is pre-shaped as it is with the parts Y and Z at the pressurized part of the piston means 92. A hinge XY is shown between part X and part Y of the skin. Part X has an average angle rn with the central axis 19 of the pressurized chamber 90. Part Y and Z are connected to each other and have an in- between angle κι, which is chosen so that the forces will be directed mainly to the piston rod. The angle λ between parts Y' and Z', and is chosen so that the higher the force in the chamber, the more this part is perpendicular to the central axis. Hinge ZZ between the half of part Z. The sealing edge 102.

Fig. 108C shows the piston at the end of a stroke. Part X' of the skin has now an angle η₂ with the central axis, while parts X' and Y' has an in-between angle κ₂, and an approximately unchanged angle λ between Y' and Z'. The angle between the half parts of part Z is approximately zero. The distance a' between the sealing edge 102 and the central axis 19 of the chamber in the shown transversal cross-section is approximately 40% of the distance a at the beginning of the stroke. The sealing edge 102' and compressed medium 103'.

Fig. 109A,B,C,D show details of a combination of a pressurizing chamber with fixed dimensions and an eight embodiment of a piston which can change its dimensions. The piston is an inflatable body which fills a transversal cross-section of the chamber. During the stroke it may constantly change its dimensions on and nearby the sealing edge. The material may be a composite of an elastically deformable liner and a support means like e.g. fibers (e.g. glass, boron, carbon or aramid), fabric, filatement or the like. Depending on the fiber architecture and the total resulting loading on the piston - the piston is shown having a bit internal overpressure -it may result in approximately the form of a sphere or approximately an elleptical curve ('rugby ball'-like form) or any shape in between, and also other shapes. A decrease of the transversal cross-sectional area of e.g. the chamber causes a decrease in the size of the inflatable body in that direction and a 3 -dimensional reduction is possible due to the fiber architecture, which is based on the 'trellis-effect' where fibers are shearing layerwise independendy from each other. The cover is also made of an elastically deformable material, suitable for the specific environmental conditions in the chamber. If the liner nor the cover is impervious it is possible to use a separate bladder inside the body, as the body contains an gaseous and/or liquid media. The support means as e.g. fibers can only give strength by themselves if the pressure inside the body is bigger than outside, because these are than in tension. This pressure condition may be preferable to obtain a suitable sealing and life time. As the pressure in the chamber can change constantly, the pressure inside the body should do the same and be a bit higher, or should always be higher at any point of the pump stroke by remaining constant. The last solution can only be used for low pressures as otherwise the piston may jam in the chamber. For higher pressures in the chamber an arrangement may be necessary so that the internal pressure vary accordingly to the variations of the pressure in the chamber + should be a bit higher. This may be achieved by several different arrangements - loading regulating means - which are based on the principles to change the volume and/or pressure of a medium inside the piston and/or to change the temperature of the medium inside - other principles are possible too, as e.g. the right choice of the material of the skin of the piston, e.g. a specific rubber type, where it is E-module which defines the deformability, or the right choice of the relative amount of the compressable part of the volume inside the inflatable- body, and its compressability. Here a non- compressable medium is used inside the piston. By a change in the size of the transversal cross-sectional area at the sealing edge the volume of the piston may change, because the size of the piston in a direction of the movement is constant. This change causes the non-compressable medium to flow to or from the a spring-force operated piston inside the hollow piston rod. It is also possible that said spring- force operated piston is situated elsewhere. The combination of the pressure caused by the change of the volume of the piston and the change in the pressure due to said spring-force results in a certain sealing force. The said spring-force works as a fine-Uining for the sealing force. An improved load regulation may be achieved by exchanging the non-compressable medium by a certain combination of a compressable and a non-compressable medium, where the compressable medium works as a load regulating means. A further improvement is when said spring is exchanged by the operation force of the piston of the chamber, as it makes the retraction of the piston easier, due to a lower sealing force and a lower friction. A temperature raise of a medium inside the piston may be achieved when specifically a medium is chosen which can quickly be warmed up.

Fig. 109A shows the longitudinal cross-section of the pressurizing chamber of Fig. 108 A with the piston 146 of Fig. 109B at the beginning of a stroke, and of Fig. 109C at the end 146' of a stroke.

Fig. 109B shows a piston 146 with an inflatable body having a wall comprising fibers 130 which have a pattern, so that the inflated body becomes a sphere. Cover 131 and liner 132. An impervious bladder 133 is shown inside the sphere. The sphere is directly mounted on the piston rod 120. It is locked at one end by a cap 121, and at the other end by cap 122. The hollow channel 125 of the piston rod 120 has a hole 123 in its side inside the sphere, so that the loading means being e.g. an in compressible medium 124 contained within the sphere can flow freely to and from the channel 125 of the piston rod 120. The other end of the channel 125 is closed by a movable piston 126 which is loaded by a spring 127. The spring is mounted on a piston rod 128. The spring 127 tunes the pressure in within the sphere and the sealing force. The sealing surface 129 is approximately in a line contact with the of the adjacent wall of the chamber. The fibers are only shown schematically (in all the drawings of this application).

Fig. 109C shows the piston of Fig. 109B at the end of a stroke where the area of the cross-section is smallest. The sphere has now a much bigger sealing surface 134 which is uniform with the adjacent walls of the chamber. The piston 126 has moved in relation to its position shown in Fig. 9B, as the non-compressible medium 124' has been squeezed out of the distorted sphere. In order to minimize the friction force it is possible that the cover at the sealing surface has ribs (not shown) or may have a low-frictional coating (as well as the wall of the chamber - not shown). As none of the caps 121 and 122 can move along the piston rod 120, the trellis effect only can be a part of the material surplus of the skin. The rest shows as a 'shoulder' 135 which may reduce the life time considerably, while it increases the friction as well. The sealing edge 129'. The distance a' between the sealing edge 129' and the central axis 19 of the chamber in the shown transversal cross-section is approximately 48% of the distance a of at the beginning of the stroke.

Fig. 109D shows an improved tuning of the sealing force, by having inside the sphere an incompressible medium 136 and a compressible medium 137. The pressure of the media is regulated by a piston 138 with a sealing ring 139 and a piston rod 140 which is directly connected to the operating force. The piston 138 can slide in the cylinder 141 of the sphere. The stop 145 secures the sphere on the piston rod 140.

Figs. 110A,B,C show an improved piston where the surplus of the skin by small cross- sections of the chamber can be released which means an improved life time and less f iction. This method concerns the fact that a suspension of the piston on the piston rod can translate and/or rotate over the piston rod to a position farther from the side of the piston where there is the biggest pressure in the chamber. A spring between the movable cap and a stop on the piston rod functions as another loading regulating means.

Fig. 110A shows a longitudinal cross-section of the chamber 169 of a pump according to the invention with two positions of the piston 168 respectively 168'. Fig. 110B shows a piston with an inflatable skin with a fibers 171 in at least two layers with a fiber architecture which results in approximately a sphere - ellipsoide, when inflated. Inside the piston can be an impervious layer 172, if the skin is not tight. The media is a combination of a compressible medium 173, e.g. air, and an incompressable medium 174, e.g. water. The skin 170 is mounted at the end of the piston rod in cap 175 which is fastened to the piston rod 176. The other end of the skin is hingend fastened in a movable cap 177 which can glide over the piston rod 176. The cap 177 is pressed towards the pressurized part of the chamber 169 by a spring 178- which is squeezed at the other end towards a washer 179 which is fastened to the piston rod 176. The sealing edge 167.

Fig. HOC shows the piston of Fig. HOB at the end of the pump stroke. The spring 178' is compressed. The same is valid for the incompressable medium 174' and the compressible medium 173'. The skin 170' is deformed, and has now a big sealing surface 167'. The distance a' between the sealing edge 167 and the central axis of the chamber is approximately 43% of the distance a at the beginning of the stroke.

Figs. 111 A,B,C show a piston which has at both of its ends in the direction of movement on the piston rod a movable cap which takes the surplus of material away. This is an improvement for a piston in a one-way piston pump, but specifically is it possible now to use the piston in a dual operating pump where any stroke, also the retraction stroke, is a pump stroke. The movement of the skin during the operation is indirectly limited due to stops on the piston rod. These are positioned so that the pressure of a medium in the chamber cannot strip the piston from the piston rod.

Fig. 1 11A shows a longitudinal cross-section of the chamber with an improved piston

208 at the beginning and at the end (208') of a stroke.

Fig. 11 IB shows a nineth embodiment of the piston 208. The skin of the sphere is comparable with the one of Fig. 10. An impervious layer 190 inside is now tightly squeezed in the cap 191 in the top and the cap 192 in the bottom. Details of said caps are not shown and all kinds of assembling methods may be used. Both caps 191,192 can translate and/or rotate over the piston rod 195. This can be done by various methods as e.g. different types of bearings which are not shown. The cap

191 in the top can only move upwards because of the existance of the stop 196 inside the piston. The cap

192 in the bottom can only move downstairs because the stop 197 prevent a movement upwards. The 'tuning' of the sealing force comprises a combination of an incompressable medium 205 and a compressible medium 206 inside the sphere, a spring-force operated piston 126 inside the piston rod 195. The media can freely flow through the wall 207 of the piston rod through holes 199, 200, 201. 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, showed as a screwed assembly at the end of the piston rod 195 tightens said piston rod. Comparable stops can be positioned elsewhere on the piston rod, depending on the demanded movement of the skin.

Fig. 111C shows the piston of Fig. 11 IB at the end of a pump stroke. The cap 191 in the top is moved over a distance x" from the stop 196 while the bottom cap 192 is pressed against the stop 197. The compressible medium 206' and the non-compressible medium 205'.

Figs. 112A,B,C show an improved piston in relation to the earlier one's. The improvements have to do with a better toning of the sealing force by the loading regulating means, a reduction of friction by a smaller sealing contact surface, specifically by smaller cross-sectional area's. The improved tuning concerns the fact that the pressure inside the piston now directly is influenced by the pressure in the chamber due to a pair of pistons on the same piston rod and which is by that independent of the existence of an operation force on the piston rod. This may be specifically advantageous during a stop in the pump stroke, if the operation force would change, e.g. increase, because the sealing force remains constant and no loss of sealing occurs. At the end of a pump stroke when the pressure in the chamber is decreased, the retraction will be more easy due to lower friction forces. In the case of a dual operating pump, the loading regulating means may be influenced by both sides of the piston, e.g. by a double arrangenment of this load regulating means (not shown). The shown arrangement of the pistons is complying with a specification: e.g. an increase of the pressure in the chamber will give an increase of the pressure in the piston. Other specifications may result in other arrangements. The relation may be designed so that the increase can be different from a linear relation. The construction is a pair of pistons which are connected by a piston rod. The pistons may have an equal area, different size and/or a changing area.

Due to a specific fiber architecture and the total resulting loading - it is shown with a bit interna] overpressure - the shape of the piston in a longitudinal cross-section is a rhomboid figure. Two of its comers in this section work as a sealing surface, which gives a reduced contact area by smaller transversals cross-sections of the chamber. The size of the contact surface may still be increased by the existence of a ribbed outer surface of the skin of the piston. The wall of the chamber and/or the outside of the piston can have a coating as e.g. nylon or can be made of a low-friction material.

Not drawn is the possibility of a chamber which has transversal cross-sectional shapes according to e.g. those of Fig. 107F with a piston which has (in this case as an example) three separate pistons according to e.g. Fig. 112A-C which each seals in the first circular cross-sectional area (Fig. 107F top, left), each other and the boundary curve, while at another point of the longitudinal axis of the chamber each seal one of the three lobe-shaped parts and each other (Fig. 7F e.g. top, right), while at still another point each seal one of the three lobe-shaped parts only.

Fig. 112A shows a longitudinal cross-section of a piston chamber combination with a tenth embodiment of a piston 222 at the beginning and at the end (222') of a stroke in a chamber 216.

Fig. 112B shows a piston of which the main construction is described in Figs. 11B and l lC. The skin comprises at the outside ribs 210. The skin and the impervious layer 190 at the inside are squeezed at the top between an inner part 211 and an outer part 212, which are screwed together. At the bottom the similar construction exists with the inner part 213 and the outer part 214. Inside the piston there is a compressible medium 215 and a non compressible medium 219. The pressure inside the piston is tuned by a piston arrangement which is directly activated by the pressure of the chamber 216. The piston 148 in the bottom which is connected to the pressurizing chamber 216 is mounted on a piston rod 217 while at the other side another piston 149 is mounted and which is connected to a medium of the piston 222. The piston rod 217 is guided by a slide bearing 218 - other bearing types can also be used (not shown). The pistons on both sides of the piston rod 217 can have different diameters - it is even possible that the cylinder 221 in which these are moving, are exchanged by two chambers, which can be of a type according this invention - by that, the piston and/or pistons are also of a type according this invention. The sealing edge 220. The piston rod 224. Distance di between the piston 148 and orifice 223.

Fig. 112C shows the piston of Fig. 112A at the end of a stroke, while there is still high pressure in the chamber 216. Sealing edge 220'. The load regulating means 148' have a different distance from the orifice 223 towards the chamber. Piston 148' and 149' are shown positioned at a larger distance than in Fig. 112B from the orifice 223: d₂. Fig. 113A,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. Within a housing as e.g. cylinder with fixed geometrical sizes an inflatable chamber is positioned which is inflatable by a medium (a non-compressible and/or a compressible medium). It is also possible that said housing can 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 (by having e.g. a viscose non-compressible medium in the wall of the chamber and/or the right toning of load regulating means, which are similar to those which have been shown for the pistons) 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 however 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 ought to be rounded of. In the last mentioned cases it may be more difficult to provide a changing cross-sectional area, and by that, a designable operation force. The wall of the chamber may be equipped with all the already shown loading regulating means the one showed on Fig. 112B, and if necessary with the shape regulating means. The velocity of the piston in the chamber may have an effect on the sealing.

Fig. 113 A shows piston 230 at four positions of the piston in a chamber 231.

Around an inflatable wall a housing 234 with fixed geometrical sizes. Within said wall 234 a compressible medium 232 and a non-compressible medium 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 different from the one shown.

Fig. 113B shows the piston after the beginning of a stroke. The distance from the sealing edge 235 and the central axis 236 is z_\. The angle ξ between the piston sealing edge 235 and the central axis 236 of the chamber. The angle v between the wall of the chamber and the central axis 236. The angle v is shown smaller than the angle ξ. The sealing edge 235 arranges that the angle v becomes as big as the angle ξ.

Other embodiments of the piston are not shown.

Fig. 113C shows the piston during a stroke. The distance from the sealing edge 235 and the central axis 236 is z₂ - this distance is smaller than zy.

Fig. 113D shows the piston almost at the end of stroke. The distance from the sealing edge 235 and the central axis 236 is z₃ - this distance is- smaller than z₂.

Fig. 114 shows a combination of a wall of the chamber and the piston which have changeable geometrical shapes, which adapt to each other during the pump stroke, enabling a continuous sealing. Shown is the chamber of Fig.l3A now with only a non-compressible medium 237 and piston 222 at the beginning of a stroke, while the piston 222" is shown just before the end of a stroke. Also all other embodiments of the piston which can change dimensions can 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.

653 DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 201 A 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. 20 IB shows the contact pressure of the piston 5* of Fig. 201 A. The piston 5* may jam at this longitudinal position.

Fig. 202A 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. 202B 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. 202C 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. 1 A, positioned into the smaller cross-section of the second longitudinal position.

Fig. 202D 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. 203A shows the piston 5 of Fig. 201A, and the deformed piston 5"* when pressurized to the same pressure level of that of piston 5* of Fig. 201 A. 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. 203B shows the contact pressure. The piston 5"* may jam at this longitudinal position.

Fig. 204A 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 chosen lower than that in the meridian direction (in the longitudinal direction of the chamber). -

Fig. 204B shows the contact pressure on the wall of piston 15'*. This results in an appropriate friction force (4.2 kg), and suitable sealing.

Fig. 204C 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. 204D shows the contact pressure on the wall of piston 15"*. This results in an appropriate friction force (0.7 kg) and a suitable sealing.

Therefore, it is possible to sealingly move a piston comprising an elastically deformable container from a smaller to a bigger cross-sectional area while having the same internal pressure - within the limitations for the diameters of the cross-sections which were chosen in this experiment.

Fig. 205 A 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. 205B shows the contact pressure of the piston 15'* of Fig. 205 A. This is low enough to allow movement (friction force 4.2 kg) and suitable for sealing.

Fig. 205C 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. 205D shows the contact pressure of the piston 15"* of Fig. 205C. This is low enough to allow movement (friction force 3.2 kg) and suitable for sealing.

Therefore, when applying a chamber pressure on a piston comprising a pressurized elastically deformable container, it is possible to sealingly move as well, at least at the longitudinal position with the smallest cross-sectional area. The stretchin due to the applied chamber force is big and it may be necessary to limit this. Figs. 206-209 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. TThe reinforcement may also be positioned outside the piston.

All kinds of fluids may be used - a combination of a compressible and a non-compressible medium, a compressible medium only or a non-compressible medium only. As 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. In order to keep the pressure in the chamber, 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. 206A 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 central axis 184 of 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. During the stroke starting at the second longitudinal position of the chamber 186, 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. Depending on the pressure in the chamber 186, there still may occur a longitudinal stretching of the wall of the container, due to pressure in the chamber 186. 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). During the stroke 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. 206B 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 flexible material, which may be e.g. a rubber type or the like, with a textile reinforcement 189, which allows expansion and contraction. The direction of the textile reinforcement in relation to the central axis 184 (= braid angle) is different from 54°44'. 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. It is tightly squeezed in the cap 191 in the top and the cap 192 in the bottom of the container 208,208'. 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 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 cornmunicating 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 tightens said piston rod. Comparable stops may be positioned elsewhere on the piston rod, depending on the demanded movement of the wall of the container. The contact area 198 between the wall of the container and the wall of the chamber. Fig. 206C shows the piston of Fig. 206B at the second longitudinal position of the chamber. The cap 191 in the top is moved over a distance a¹ 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 compressible fluid 206' and the non-compressible fluid 205'.

Fig. 206D 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'. When the material type and thickness is the same for all layers, and the number of layers even, while the stitch sizes for each direction are equal, the expansion and contraction of the wall of the container may be equal in the XYZ-direction. When expanding the stitch ss and tt, respectively in each of the directions of the matrix will become bigger, while contracting these wil become smaller. As 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. 206B.

Fig. 206E is a 3-dimensional drawing and shows the reinforcement matrix of Fig. 206D 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. 206D.

Fig. 206F 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. When the wall of the container is expanding the inelastic material (but elastically bendable) may limit the maximum expansion of the wall 187 of the container 217. It may be necessary to stop the movement of the container 217 over the piston rod 195 by e.g. stop 196, so that sealing may remain. The lack of such a stop 196 may give the possibility of creating a valve. Fig. 206G is a 3 -dimensional drawing and shows the reinforcement matrix of Fig. 206F 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. 206F.

Fig. 206H shows three stages I, Π and III of a production process of the piston comprising an elastically deformable container. Over a rod 400 is a rubber manchet 401 positioned, over which a reinforced manchet 402 e.g. according to those of Fig. 406E-G is positioned. Over the last mentioned another rubber manchet has been positioned.-Between-the machet 401 and the rod one or more caps 404 may be positioned. All may slide over the rod 400. The rod 400 may be hollow and may be connected to a high pressure steam source. Stage II: the pressurized steam may enter the cave 408 of the oven 406 by outlets 405 which may be positioned at the end of the rod. A piece of the complete rubber/rein forcement manchets 407 may be cut and transported over the rod 400 into the cave 408. 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 404. The manchet 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 (III). 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 manchets 407 may take place before the vulcanisation. The rod 400 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 manchet 407 and vulcanize it. This may be archived 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. 207A 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. 207B 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. The direction of the fibers in relation to the central axis 184 (= braid angle) may be different from 54°44'. The contact area 211 between the wall 218 of the container 217 and the wall 185 of the chamber 186. Due to the expansion the thickness of the wall of the container may be smaller, but not necessarily very different than that of the container as produced when positioned at the second longitudinal position. 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.

During the stroke the pressure inside the container 217,217' may remain constant. It may also be possible that the pressure changes during the stroke. The timing of the sealing force may comprise a combination of an incompressible fluid 205 and a compressible 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. 210), 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 tightens said piston rod. Fig. 207C shows the piston of Fig. 207B at the second longitudinal position of the chamber 186. The contact area 21 V, which is small. The cap 1 1 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 compressible fluid 206' and the non-compressible fluid 205' which may have changed volume in the container.

Figs. 208A,B,C deal with the construction of the piston which may be identical with that of Figs. 207A,B,C with the exception that 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. 208A 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. 208B 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. 208C 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. 208D shows a top view of the piston 228 and 228', respectively with the reinforcement means 223, and 223" respectively at the first and second longitudinal position of the chamber 186 respectively.

Fig. 208E 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 lie in planes through the central axis 184 in the longitudinal direction of the chamber 186. Fig. 208F 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. 208G shows schematically how fibers 402 may be mounted in caves 431 of the cap 430. This may be achieved by rotating the cap and the fibers around the central axis 433, each may have its own velocity, while the fibers 432 are being pushed towards and in the caves 431.

Fig. 209A 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. 209B 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'. The contact area 253.

Fig. 209C shows the longitudinal cross-section of the piston 258'. The contact area 253'.

Figs. 210-212 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 mamlaining 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. by a combination of the second enclosed space and a piston herein, so that the force on the piston in the first enclosed space remaines equal, while the force on the piston in the second enclosed space reduces, when the pair of pistons moves towards the first enclosed space e.g. when fluid is moving from the first enclosed space into the container. This complies well with p.V = constant in the second enclosed space. 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. In order to enable inflation, 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. Moreover, combined with a valve with a spring-force operated valve core, the valve closes automatically when equal pressure levels has been obtained.

If 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.

In the case that the pressure level in the pressure source is higher of that of the container it may be necessary that during the stroke the flow between the pressure/volume source and the container may be steered by means of valves. These 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.

Having a valve communicating with the chamber, it may enable automatic inflation of the container, when the pressure in the container is lower than the pressure in the chamber. When this may not be the case, such 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. 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. 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 kind 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 predeterrriined value of the pressure, e.g. to the space above the container or to the chamber. Another option may be that the 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. Another option may be that the 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. Or, by combining the piston 292 of Fig. 21 IE with means so that the piston opens the channel 297 when a certain pressure has been reached (not shown).

Fig. 21 OA 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. 206A-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 flexible 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 (not drawn) which may be adjusted to a certain pre-determined value of the pressure. The released fluid may be directed to the chamber 209 and/or to the space 251.

Fig. 210B shows an alternative option for the inflation valve 241. Instead of the inflation valve 241 in the handle 240, only a bushing 244 without a valve core 245 may be present, which enables connection to a pressure source.

Fig. 2 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. The stop 249.

Fig. 210D shows details of the flexible piston 126 of the check valve 242. The spring 248 keeps the pressure on the piston 126.

Fig. 210E shows the pressure source 451 which may have a pressure which exceeds the pressure level of the container. Inlet valve 452 with e.g. a valve actuator 453 (the configuration 459 shown is analogous to the one of Fig. 21 IE (292,297)), and outlet valve 454 with e.g. a valve actuator 455 (the configuration 451 shown is analogous to the one of Fig. 21 IE (292,297)). The space 460 is connected to the chamber 457, while the space 462 is connected to the chamber 458. The valves 452 and 454 may be mounted in the piston rod 456, which may be updivided in two chambers 457 and 458.

Fig. 21 OF shows the construction of Fig. 210E where two black boxes are shown comprising each a valve arrangement which may be steerable by external signals. The steering 415 may receive pressure signal 416 and 417, respectively from the inside of the piston at different longitudinal positions of the chamber. The steering 415 may send signals 418 and 419, respectively to the actuator 422 of the outlet valve arrangement 420 and to the actuator 423 of the inlet valve arrangement 421. This valve and valve steering arrangement may be analogously to the one shown in Fig.21 IF.

Fig. 211 A 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. 206A-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. 210A,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. In order to manually control the outlet valve 263, the foot 262 may be equipped with a pedal 265 which can turn an angle a around an axle 264 on the foot 262. The pedal 265 is connected to a piston rod 267 by an axle 266 in a non-circular hole 275 in the top of the pedal 265. The foot 262 has an inlet valve 269 (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.

Fig. 21 IB 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. The piston rod 195 of the piston type container 248,248' with internal wall 194. Pistons 242,270 seal on internal wall 194.

Fig. 211C shows an alternative wall 273 of the piston rod 272 of the piston type container 248,248' which has a angle β with the central axis 184 of the chamber 186. 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. 21 ID 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. When the core pin 245 is not depressed, 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. The chamber 186.

Fig. 21 IE 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 bearing 293 for the piston rod 267 of the piston 292. The piston rod 267 may be connected to the pedal 265 (Fig. 211 A) or to other actuators (schematically shown in Fig. 211 E).

Figure 211 E ' is being treated after Fig 218B .

Fig. 21 IF shows the piston 248' and the inflation arrangement 368 of Fig. 21 ID, besides the arrangement 369 to control the outlet valve of Fig. 21 IE. The inflation arrangement 368 comprises now also the arrangement 370 to control the valve of Fig. 21 IE. This may be done to enabling the closing of the valve, when the predetennined 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.

When the chamber has a lower working pressure than the pre-determined value of the pressure in the piston, 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 predetermined pressure.

Fig. 211G 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 tightly closed. The contact area 313 of the cap 312 with the cylinder 282 (fig. 21 ID). When the force on the cap 312 from the chamber becomes bigger, the cap may move to a position where the cap 312' is shown, until there is equivalence of the forces on the cap by the medium/media of the chamber. The spring 310 may determine the maximum value of the pressure to depress the valve core pin 245. A Schrader valve 260.

Fig. 212 shows an elongated 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.

Figs. 213A,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. Within a housing as e.g. cylinder with fixed geometrical sizes an inflatable chamber is positioned which is inflatable by a fluid (a non-compressible and/or a compressible 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 (by having e.g. a viscose non-compressible fluid in the wall of the chamber and/or the right tuning of load regulating means, which may be similar to those which have been shown for the pistons) 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 however 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. In the last mentioned cases it may be more difficult to provide a changing cross-sectional area, and by that, a designable operation force. The wall of the chamber may be equipped with all the already shown loading regulating means the one showed on Fig. 212B, and if necessary with the shape regulating means. The velocity of the piston in the chamber may have an effect on the sealing.

Fig. 213 A shows piston 230 at four positions of the piston in a chamber 231.

Around an inflatable wall a housing 234 with fixed geometrical sizes. Within said wall 234 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 different from the one shown.

Fig. 213B shows the piston after the beginning of a stroke. The distance from the sealing edge

235 and the central axis 236 is z_\. The angle ξ between the piston sealing edge 235 and the central axis

236 of the chamber. The angle v between the wall of the chamber and the central axis 236. The angle v is shown smaller than the angle ξ. The sealing edge 235 arranges that the angle v becomes as big as the angle ξ. Other embodiments of the piston are not shown.

Fig. 213C shows the piston during a stroke. The distance from the sealing edge 235 and the central axis 236 is z₂ - this distance is smaller than z_\.

Fig. 213D shows the piston almost at the end of stroke. The distance from the sealing edge 235 and the central axis 236 is z₃ - this distance is smaller than z₂.

Fig. 214 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. 213 A now with only a non-compressible medium 237 and piston 385 at the beginning of a stroke, while the piston 385' 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. 215A-F show embodiments of the chamber with cross-sections of different sizes which have constant circumpherential sizes. This is another solution for the jamming problem of the cited pistons of WO 00/70227. 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. 208D approximately parallel with the central axis of the chamber, and when the reinforcement is made of e.g. elastical threads (Figs. 206D, 206E), or those shown in Figs. 206F, 206G allowing each an individual size. The one showed in Figs. 209A, 209B may also function well. 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 jarnming, 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. If the change of the area of a transversal cross-section of the piston and/or the chamber between two positions in the direction of movement is continuous but still so big that this results in leakages, it is advantageous to minimize the change of the other parameters of the cross-section. This can be illustrated by using e.g. a circular cross-section (fixed shape): the circumference of a circle is D, while the area of a circle is ¼ π D² (D = diameter of the circle). That is to say, a reduction of D will only give a linear reduction of the circumference and a quadratic reduction of the area. It is even possible to also maintain the circumference and only reduce the area. If also the shape is fixed e.g. of a circle there is a certain minimum area. Advanced numeric calculations where the shape is a parameter can be made by using the below mentioned Fourier Series expansions. 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: where

cp = - \^* ₀ f (x)∞s(px) dx

π d_p = - \₀" f (x) sm(px) dx

K

0≤χ≤2π, x e N p≥0 , p c_p = cos-weighted average values of f(x),

d_p = sin-weighted average values off(x),

p = representing the order of trigonometrical fineness

Figs. 215A, 215E 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. As an example: Fig. 215F 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. By using a starting area, and a starting boundary-length it is possible to count on a smallest possible curvature for a certain desired target area.

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 215A, 215E, 215F 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). One characteristic of these curves is that when a line is drawn from the mathematical pole which lies in the section plane it will intersect the curve at least one time. The curves are symmetrical towards a line in the section plane, and could also have been generated by the single Fourier Series expansion which follow. A piston or chamber will be more easy to produce when the curve of the transversal cross-section is symmetric with reference to a line which lies in the section plane through the mathematical pole. Such regular curves can approximately be defined by a single Fourier Series expansion: f ( x ) = ^ +∑c_p cos (px)

* p-l

where

p≥0 , p e ¾, c_p = weighted average values off(x),

p = representing the order of trigonometrical fineness.

When a line is drawn from the mathematical pole it will always intersect the curve only one time.

Specific formed sectors of the cross-section of the chamber and/or the piston can approximately be defined by the following formula: f ( x ) = ^ +∑c_P∞s (3px)

* p-l where

6 £

c_P = ^~ f (x)∞s(3px) dx

TV

c_p = weighted average values off(x),

p = representing the order of trigonometrical fineness

where

r₀≥0,

a^{≥ 0>} <fl>

m≥0, m e IS.

« > 0, « 6 ¾

0 < φ < 2π, and where

r - the limit of the "petals" in the circular cross section of the activating pin, ro = the radius of the circular cross section around the axis of the activating pin, a = the scale factor for the length of the "petals",

Tmax = r₀ + a

m = the parameter for definition of the "petal" width

n = the parameter for definition of the number of "petal " φ = the angle which bounds the curve.

The inlet is positioned close to the end of the stroke due to the nature of the sealing portion of the piston means.

Fig. 215 A 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. 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.

Fig. 215B shows a longitudinal cross-section of the chamber 162, of which the transversal cross-sectional area changes by remaining circumference along the central axis.

Fig. 215C shows transversal cross-section H-H 152 of Fig. 207G 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. 215D shows a transversal cross-section I-I of Fig. 207G 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. Also shown is the smallest part of the chamber. Fig. 215E 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. This series show decreasing area's of the transversal cross-section, but it is also possible to increase these areas by remaining the circumference constant. 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 size of the cross-sectional area bottom right is approximately 49% of the starting area size left, top.

Fig. 215F 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 > is determined by: where r — smallest radius of curvature

L = boundary-length = constant

A; = decreased value of the starting domain area Ao

As an example from Fig. 203D: Domain area Ao = π(30)² and boundary length L = 60π = 188.5 corresponding to the area and boundary length of a disk of radius 30. The length is required to be constant, but the area is decreased to the value Aj to be specified. The desired final configuration should have the area Ai = π (19/2)² = 283.5. The convex curve with the smallest possible curvature of the boundary curve is now: r 1.54

K l/r = 0.65

x 89.4

The curve may further be optimised by exchanging the straight lines by curves which may improve the sealing of the piston to the wall.

Fig. 216 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. 217A shows a convex chamber 380 within a wall 381. "s" means stroke.

Fig. 217B shows the Force-Stroke diagram in the direction shown in Fig. 217A.

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. 218A shows an example of a Movable Power Unit 390, shown movable by parachute 391, and by wheels 392.

Fig. 218B shows the Movable Power Unit 390, with a power unit comprising a set of solar cells 393 on top and a motor 394. Moreover a water pump 395, and a compressor 396. The steering unit 397.

Fig. 21 IE' shows an adaptation to the outlet valve depicted in Fig. 21 IE. The piston rod 267 is connected to a second channel pin 8001. Said channel pin is installed in guiding channel 8002. The channel pin closes the equalisation channel 8003. Said channel pin has a hole, which allows a flow through channel 8003 when the piston rod 267 pushes piston 292 in opening 308 of channel 297. Said equalisation channel connects the channels 305, 306, 307 in the valve with an outflow chamber 8004. Said outflow chamber may be the outflow chamber of the valve. This arrangement is used when the pressure build up in the valve's inflow chamber is unsufficient to activiate the valve and the low pressure from the outflow chamber of the valve may be used to trigger the activation of the valve.

507 DESCRIPTION OF PREFERRED EMBODIMENTS

Figure 301 shows a valve actuator in a clip-on valve connector to be coupled to e.g. a Schrader valve. The piston 477 is very near the first end 492 of the cylinder 470. The connector has a housing 500 and the sealing means comprises one annular portion 475. The securing means comprises temporary thread 476. The housing also has a center axis 479 and a coupling section 510.

Figure 301 A shows an enlarged detail of Figure 301. The cylinder 470 has a cylinder wall portion 511 with a diameter which fits the piston ring 508 of the-piston 477. Near its first end- 492, the cylinder wall comprises enlargement wall portions 475a, 475b, 476a with an enlarged diameter, comprising flow channel portions 471,472,473 around the piston means 477,508 when the activating pin has enough opened the core of the valve. The flow from the pressure source to the valve can now be established. The first end 492 of the cylinder 470 functions here as a stop for the movement of the activating pin. The channel portions 473 and 474 are parts of the piston control means 476c. These parts can have several shapes which depend on the chosen production technique: e.g., channel portions 473,474 as sector parts of a circle and (507) as cylinders made by injection moulding, while alternatively channel portions (507) could also be drilled holes. Channel portions 473,474 could be considered 'flow shaped', and are constructed to reduce aerodynamic drag. The inclined enlargement wall portion 475a has an angle τ with the center axis 479, which is larger than 0° and smaller than 20°, normally in the interval 1°< τ < 12° with respect to the direction of the gaseous and/or liquid medium or media, respectively coming from the pressure source. The piston control means 476c has three grooves with walls 476a and 476b, respectively. The wall 476a has an angle ω which is larger than 0° and smaller than 20° (usually in the interval between 6° and 12°) with respect to the direction of the gaseous and or liquid medium or media corning from the pressure source. The alternative for the forementioned channel portions 473 and 474 are channels (507) where the piston control has no grooves. In this alternative, a hole (507) parallel to the center axis 479 and beside the piston control connects channel portion 475b (shown as three holes with dotted lines) and the coupling hole.

Figure 30 IB shows section G-G from Figure 301 A, with the channel portions 473 and 474 and the stopper 492. The alternative channel portion (507) is sketched by dotted lines.

Figure 302 shows a valve actuator in a universal clip-on valve connector with the housing 504 and with a sealing means comprising a first annular portion 482 and a second annular sealing portion 483 situated coaxially with the center axis 486 of the coupling section, in the direction of the center axis 486 of the coupling section 503. The first annular sealing portion 482 is closer to the opening 502 of the coupling section than the second annular sealing portion 483, and the diameter of the first annular sealing portion 482 is larger than the diameter of the second annular sealing portion 483. The coupled valves can be secured by at least one 'clip' (= i.e. temporary thread) 476. However, two clips 493 opposite each other are preferable. A taper cone 501 near the sealing surface 482 helps center the valve. The taper cone has an angle ω with the center axis 486, and normally this angle is > 45°. A separate cylinder sleeve 496 with cylinder wall portion 509 is shown which is sealed. It is fastened by for example a snap-lock 497 in the wall of the housing 504. This is an economical way of making the negative slip angle of the inclined enlargement wall portion 512 possible. The cylinder sleeve 496 has distant from the piston stop 495 an angle ς, so that the piston ring 508 is non-sealing there.

Figure 302A shows the channel portions 480 and 481 respectively defined by the enlargement wall portions 487 and 488 of the piston control means, respectively. The activating pin is streamlined with the piston 484 and the piston rod 485. The wall portion 487 has an angle κ with the center axis 486 seen in the direction of the medium coming from the pressure source, which is larger than 0° and smaller than 20° (usually in the interval between 6° and 12°). The stepped surface 498 of wall of housing 504 makes an air tight connection from the wall of the cylinder sleeve 496 to the cylinder 499. It is of course also possible to make the air tight connection on the other side of the cylinder. In the bottom of the cylinder sleeve 496 is the inclined enlargement wall portion 512 shown which together with the piston ring 515 forms channel portion 471.

Figure 302B shows section H-H of Figure 302 A and the stopper 495 for the movement of the activating pin. Also shown is the wall portion 488 and the channel portion 481.

Figure 303 shows an activating pin which is comparable of the one from Figure 301. The piston 529 is also shown. The piston rod 531 need not to be sealed against the piston control.

The cylinder 536 of the valve actuator is within housing 532 of the valve connector.

The coupling section 530 is also shown.

Figure 303A shows a channel portion 533 with an expansion 535 and a channel portion 534 formed as a radial drilling 534. The piston ring 539 opens and closes this conducting channel at its orifice 537, depending on the position of the activating pin. The direction of the channel portion 534 in relation to the center axis is comparable with the angle τ of channel portion 471 of Fig. 301 A. The wall of expansion 535 has an angle comparable to angle ω of the wall 476a Fig. 1A. Also shown is the cylinder wall portion 538 of the cylinder 536.

Figure 304 shows an activating pin and its cylinder, which was shown in Figure 301. This is built in an assembled pipeline housing means 520,521 or the like, in which a valve 522 with a spring- force operated core pin 523 is situated, e.g. a Schrader valve. The activating pin is engaging with the core pin 523 of the valve.

Figure 305 shows a valve actuator in a universal valve connector. It is comparable with the one of Figure 301. However, two sealing means 540, 541 with an in-between distance A can seal two valves of different sizes. Two enlargements 1 and 2 of the diameter of the cylinder 542 in the cylinder wall 550 are shown, with the in-between distance B. An activating pin 543 is also shown, with two engaging levels on a distance B. The in-between distances can be equal or different if for example the valves are of a different type, so that the distance from the core pin to the sealing is not the same. Between the two enlargements 1 and 2 is a cylindrical wall portion 544, with cylinder portion 545, which fits the piston ring 508. Also is shown the center axis 546, the coupling section 547 and its opening 548 from the housing 549.

19597 DESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 401 A shows line XX between two of the three engaging surfaces 1,2 of the basis 4 with a rigid surface 5, around which the combination 6 may move. The line Y-Y between two of the three engaging surfaces 2,3 of the basis 4 with a rigid surface 5, around which the combination 6 may move. The line Z-Z between two of the three contact points 1,2 of the basis 4 with a rigid surface 5, around which the combination 6 may move.

Fig. 40 IB shows the combination 6, comprising a hamber 7, a guiding- 8 for the piston rod 9, a handle 10. The basis 4 with contact points 1, 2 and 3, which are rounded off towards the rigid surface. The chamber 7 is rigidly connected to the basis 4 by means of reinforcement 11.

Fig. 402 A shows the handle 10 of the combination 6 when the combination 6 is in

its rest position 12.

Fig. 402B shows the combination 6 in its rest position 12, when the transition 13 between the combination 6 and the reinforcement 14 of the basis 40 is in its rest position. The transition 13 may be made of a flexible material, and is positioned around the chamber 7.

Fig. 402C shows the activated position 14 of the handle 0, when the handle 10 has been moved from its rest position 12 at the front side of the said rest position.

Fig. 402D shows the activated position 15 of the handle 10, when the handle has been moved from its rest position 12 at the back side of the said rest position.

Fig. 402E shows the activated position 16 of the handle 10, when the handle has been moved from its rest position 12 at the left front side of the said rest position.

Fig. 402F shows the activated position 17 of the handle 10, when the handle has been moved from its rest position 12 at the left back side of the said rest position.

Fig. 402G shows the activated position 18 of the handle 10, when the handle has been moved from its rest position 12 at the right front side of the said rest position.

Fig. 402H shows the activated position 19 of the handle 10, when the handle has been moved from its rest position 12 at the right back side of the said rest position.

Fig. 403A shows a floor pump where the transition between the chamber 7 and the basis 4 is an elastically deformable bushing 20.

Fig. 403B shows an enlargement of the transition between the chamber 7 and the basis 40. The chamber 7 has a protrusion 21 which complies with a groove 22 in the bushing 20, enabling a simple mounting of the chamber 7 in the base 40. The protrusion 41 on top of the reinforcement 42 of the basis 40.

Fig. 403C shows a floor pump where the transition between the chamber 7 and the basis 4 is an elastically deformable bushing 23.

Fig. 403 D shows an enlargement of the transition between the chamber 7 and the 40. The chamber 7 has a groove 25 which complies with a protrusion 24 in the bushing 23, enabling a simple mounting of the chamber 7 in the basis 40.

Fig. 404A shows the combination 6 in the form of a floor pump with a cab 25 which allows a transversal translation and/or deflection of the piston rod in relation to the rest of the combination 6 and the basis 43. The basis 43 may be directly, by means of the reinforcement 42, or indirectly e.g. by means of a flexible bushing be connected to the basis 41.

Fig. 404B shows an enlargment of the cap 25 of Fig. 404A, when the piston 44 is at the end of a stroke farthest from the basis 43. The piston rod 9 is moving in a guiding means 26, of which the convex contact inner surface 31 is in line contact at its centre line 27 with the piston rod 9. The guiding means 26 is being held within the cap 9 by surfaces 36 and 37, and by a flexible O-ring 28. The cross- sectional area of the space 29 between surfaces 36 and 37 of the cap 9 and the guiding means 26 is shown bigger than the cross-sectional area of the ring 28 itself, so as to make a substantial compression of the ring 28 possible (see e.g. Fig. 404C). The distance a between the outside of the piston rod 9 and the wall 38 of the spaces 33 and 34 of the cab 9. Said distance a may be approximately the same distance b between the piston rod and the wall 38 of the cab 9 in the top of the cab.

Fig. 404C shows Fig. 4B where the centre axis 32 of the piston rod 9' is deflected angle a in relation to the centre axis 30 of the rest of the combination. The space 29' is almost being filled up by the compressed ring 28', which is compressed by the translated guiding means 26'. The space 34'. The space 33'. The contact surface 35 between the guiding means 26' and the piston rod 9'. Distance a' is smaller than distance a of Fig. 404B.

Distance b' is smaller than distance b of Fig. 404B, and more than the difference between distances a and a'.

Fig. 404D shows an enlargement of the cap 25 of Fig. 404A, when the piston 44 may be at the end of a stroke closest to the basis 43. The centre line 30 of the combination. The spaces 33 and 34 between the inner walls 38 of the cab 25 and the piston rod 9.

Fig. 404E shows Fig. 404D when the piston rod 9' is translated to the left, to a distance a" between the outside of the piston rod 9' and the inner wall 38 of the cab 25. The guiding means 26" is moved to the left, compressing the ring 28" - shown is that the space 29" has been filled up in this cross-section by the compressed ring 28". The space33" is approximately equal the space 34" with a distance a" which is equal distance b" which is smaller than distance a.

Fig. 405 A shows the left portion 51 of the handle 52 and the right portion 53 of the handle 52, in relation to the centre axis 54 of the combination 55. The angle a between the centre axis 56 of the left portion 51 of the handle 52 and the centre axis 57 of the right portion 53 of the handle 52 is less than 180°, when viewing from the position X-of the user. The center point 61 of the left portion 51 and center point 62 of right portion 53.

Fig. 405B shows the a front view of the floor pump of Fig. 5 A, comprising the handle 52 and the combination 55. Handle 52 with the left 51 portion and the right 53 portion. The centre axis 54 of the combination 55.

Fig. 406A shows the left portion 58 of the handle 59 and the right portion 60 of the handle 59, in relation to the centre axis 54 of the combination 55. The angle β between the centre axis 56 of the left portion 58 of the handle 59 and the centre axis 61 of the right portion 60 of the handle 59 is more than 180°, when viewing from the position X of the user.

Fig. 406B shows the a front view of the floor pump of Fig. 406A, comprising the handle 59 and the combination 55. The handle 59 with the left 58 portion (= turned around right portion 53) and the right portion 60 (= turned around left portion 51).

507 SUMMARY OF THE INVENTION

The present invention provides a valve actuator which comprises an inexpensive combination of a cylinder, within in which the piston driving the activating pin moves, and an activating pin, having a simple construction. This combination can be used in stationary constructions, such as chemical plants, where the activating pin engages the spring-force operated core pin of a valve (e.g. a release valve), as well as in valve connectors (e.g. for inflating vehicle tires). The disadvantage of conventional valve connectors have been overcome by the valve actuator of the present invention. This valve actuator features a piston having a piston ring fitting into the cylinder, where the piston, in its first position, is at a first predetennined distance from the first end of the cylinder. In the piston's second position, it is at a second predetermined distance from the first end of the cylinder, wherein the second predetermined distance is larger than the first predetermined distance. The cylinder wall comprises a conducting channel for allowing conduction of gaseous and/or liquid media between the cylinder and the coupling section when the piston is in the first position, whereas conduction of gaseous and/or liquid media between the cylinder and the coupling section is inhibited by the piston when the piston is in the second position.

Another embodiment of the present invention according to claim 10 features a conducting channel through a part of the body of the valve actuator. The channel forms a passage for gaseous and/or liquid media between the cylinder and the part of the valve actuator which is coupled to the valve. The orifice of the channel opening in the cylinder is located such that, when the piston is in the first position, pressurized gaseous and/or liquid media flowing from the pressure source to the cylinder may flow further through the channel to the valve to be actuated. When the piston is in the second position, it blocks the cylinder so that the flow of pressurized gaseous and/or liquid media into the channel is not possible.

The various embodiments described above are provided by way of illustration and should not be constructed to limit the invention. Those skilled in the art will readily recognize various modifications and changes which may be made to the present invention without strictly following the exemplary embodiments and applications illustrated and described herein, and without departing from the true spirit and scope of the present invention as claimed.

Claims

CLAIMS 19627 01-07-2012

1. A piston-chamber combination comprising a chamber (162,186,231) which is bounded by an inner chamber wall (156,185,238), and comprising an actuator piston inside said chamber to be engagingly movable relative to said chamber wall at least between a first longitudinal position and a second longitudinal position of the chamber,

said chamber having cross-sections of different cross-sectional areas and different circumferential lengths at the first and second longitudinal positions, and at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longitudinal position,

said actuator piston comprising a container (208,208', 217,217', 228,228', 258,258',

450,450') which is elastically deformable thereby providing for different cross-sectional areas and circumferential lengths of the piston adapting the same to said different cross-sectional areas and different circumferential lengths of the chamber during the relative movements of the piston between the first and second longitudinal positions through said intermediate longimdinal positions of the chamber,

the actuator piston is produced to have a production-size of the container (208,208' ,217,217',228,228',258,258',450,450') in the stress-free and undeformed state thereof in which the circumferential length of the piston is approximately equivalent to the circumferential length of said chamber (162,186,231) at said second longitudinal position, the container being expandable from its production size in a direction transversally with respect to the longitudinal direction of the chamber thereby providing for an expansion of the piston from the production size thereof during the relative movements of the actuator piston from said second longitudinal position to said first longitudinal position,

the container (208,208',217,217',228,228' ,258,258',450, 450') being elastically deformable to provide for different cross-sectional areas and circumferential lengths of the actuator piston, characterized by the fact that • the combination comprises means for introducing fluid from a position outside said container into said container, thereby enabling pressurization of said container, and thereby expanding said container,

• a smooth surface of the wall of the actuator piston, at least on and contineously until nearby its contact area with the wall of the chamber,

thereby displacing said container from a second and to a first longitudinal position of the chamber.

2. A piston-chamber combination comprising a chamber (162,186,231) which is bounded by an inner chamber wall (156,185,238), and comprising an actuator piston inside said chamber to be engagingly movable relative to said chamber wall at least between a first longitudinal position and a second longitudinal position of the chamber,

said chamber having cross-sections of different cross-sectional areas and different circumferential lengths at the first and second longitudinal positions, and at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longimdinal position,

said actuator piston comprising a container (208,208',217,217' ,228,228', 258,258' ,

450,450') which is elastically deformable thereby providing for different cross-sectional areas and circumferential lengths of the piston adapting the same to said different cross-sectional areas and different circumferential lengths of the chamber during the relative movements of the piston between the first and second longitudinal positions through said intermediate longitudinal positions of the chamber,

the actuator piston is produced to have a production-size of the container (208,208',217,217' ,228,228' ,258,258' ,450,450') in the stress-free and undeformed state thereof in which the circumferential length of the piston is approximately equivalent to the circumferential length of said chamber (162,186,231) at said second longitudinal position, the container being expandable from its production size in a direction transversally with respect to the longitudinal direction of the chamber thereby providing for an expansion of the piston from the production size thereof during the relative movements of the actuator piston from said second longitudinal position to said first longitudinal position, the container (208,208', 217,217', 228,228', 258,258', 450, 450^*) being elastically eformable to provide for different cross-sectional areas and circumferential lengths of the actuator piston, and comprising an enclosed space,

characterized by the fact that

· the combination comprises means for changing the volume of the enclosed space communicating with said actuator piston of said container from a position outside said container, thereby enabling pressurization of said container, and- thereby expanding said container,

and thereby displacing said container from a second to a first longitudinal position of the hamber.

3. A piston-chamber combination according to claim 1 or 2, wherein said actuator piston inside or outside said chamber to be sealingly movable relative to said chamber wall.

4. A piston-chamber combination according to claim 1, 2 or 3, wherein a part of said chamber, positioned adjacent to said actuator piston are communicating with each other through a channel or through the atmosphere.

5. A piston-chamber combination according to any of claims 1- 4, wherein the chamber is elongate.

6. A piston-chamber combination according to any of claims 1-4, wherein the chamber is circular.

7. A piston-chamber combination according to claim 6, wherein the chamber is formed around a circleround centre axis.

8. A piston-chamber combination according to claims 1-7, wherein the actuator piston is

depressurized and not engaging with the wall of the chamber.

9. A piston-chamber combination according to claim 8, wherein the piston is moving from a first to a second longitudinal position of the chamber.

10. A piston chamber combination according to claims 1-7, wherein a part of the lengh of the wall of

the chamber is parallel to the centre axis of said chamber.

11. A piston chamber combination according to claim 10, wherein said wall of the chamber is positioned at an end of a stroke of the actuator piston.

12. A piston-chamber combination according to claims 1-7, wherein the container (208, 208', 217, 217', 228,228', 258,258', 450,450') is comprising a deformable material (205,206).

13. A piston-chamber combination according to claim 12, wherein the deformable material (205,206) is a fluid or a mixture of fluids, such as water, steam and/or gas, or a foam.

14. A piston-chamber combination according to claims 12 or 13, wherein in a cross-section through the longitudinal direction, the container, when being positioned at the first longitudinal position of the chamber (186,231), has a first shape which is different from a second shape of the container when being positioned at the second longitudinal position of said chamber.

15. A piston-chamber combination according to claim 14, wherein at least part of the deformable material (206) is compressible and wherein the first shape has an area being larger than an area of the second shape.

16. A piston-chamber combination according to claim 14, wherein the deformable material (206) is at least substantially incompressible.

17. A piston-chamber combination according to claims 1-7, wherein the container is inflatable.

18. A piston-chamber combination according to claims 1-7, wherein the container (208,208' , 217,217', 228,228', 258,258', 450, 450') additionally comprises an enclosed space (210,243) commu- nicating with the deformable container .

19. A piston-chamber combination according to claim 18, wherein said introduction of the fluid from a position outside said container into said container is done through a first enclosed space, which is communicating with said enclosed space.

20. A piston-chamber combination according to claims 1, 3-7, further comprising means for removing fluid from said container to a position outside the piston, thereby enabling contraction of said container.

21. A piston-chamber combination according to claim 20, wherein the removal of fluid is done through a second enclosed space, which is communicating with said enclosed space.

22. A piston-chamber combination according to claim 2-7 or 18, wherein said means are communicating with said enclosed space of said piston, by changing the volume of said enclosed space, increasing said volume and thereby depressurizing said actuator piston, thereby enabling contraction of said container.

23. A piston-chamber combination according to claim 22, wherein the piston is movable relative to said chamber wall at least from a first to a second longitudinal position of said chamber.

24. A piston-chamber combination according to claims 1-7, wherein the wall of the container (208,208', 217,217*, 228,228', 258,258', 450, 450') comprises a bendable reinforment layer,

25. A piston-chamber combination according to any of the previous claims, wherein the cross- section of the contact surface of the container and the wall of the chamber is cutting the central axis of said container in the longitudinal direction approximately just aside the middle point of said section of the elastically deformable wall of the container, at the side of a second longitudinal position.

26. A piston-chamber combination according to claim 25, wherein the cross-section of the contact surface of the container and the wall of the chamber is cutting the central axis of said container in the longitudinal direction approximately outside the middle point of said section of the elastically deformable wall of the container, at the side of a second longitudinal position.

27. A piston-chamber combination according to claims 12, 17, 20 or 22, wherein the actutor piston is comprising a piston rod, which is comprising said enclosed space.

28. A piston-chamber combination according to claim 26, wherein the piston rod is comprising engaging means outside said chamber.

29. A piston-chamber combination according to claim 28, further comprising a crank adapted - to translate the motion of the piston between second and first longitudinal positions of the chamber into a rotation of the crank.

30. A piston-chamber combination according to claim 28, wherein the crank is translating its rotation into a movement of the piston from first to second longituciinal positions of the piston.

31. A piston-chamber combination according to claims 19, 21 or 28, wherein the crank is comprising said first and said second enclosed space.

32. A combination according to claims 1-7, wherein the cross-sectional area of said chamber at the second longitudinal position thereof is 95 - 15 % of the cross-sectional area of said chamber at the first longitudinal position thereof.

33. A combination according to claims 1-7, wherein the cross-sectional area of said chamber at the second longitudinal position thereof is approximately 50% of the cross-sectional area of said chamber at the first longitudinal position thereof.

34. A combination according to claims 1-7, wherein the cross-sectional area of said chamber at the second longitudinal position thereof is approximately 5 % of the cross-sectional area of said chamber at the first longitudinal position thereof.

35. A combination according to claims 1-6, wherein said chamber comprising convex shaped walls of longitudinal cross-sectional sections near a first longitudinal position, said sections are updivided from each other by a common border, a distance between two following common borders defines a heigth of the walls of said longitudinal cross-sectional sections, said heigths are decreasing by an increasing overpressure rate of said actuator piston in relation to the pressure in said chamber, the transversal length of the cross-sectional common borders is determined by the maximum work force of said actuator piston, which is chosen constant for said common borders.

36. A combination according to claims 1-6, wherein said chamber comprising convex shaped walls of longitudinal cross-sectional sections near a first longitudinal position, said sections are updivided from each other by a common border, a distance between two following common borders defines a - heigth of the walls of said longitudinal cross-sectional sections, said heigths are decreasing in a direction from a first longitudinal postion to a second longitudinal position, the transversal length of the cross-sectional common borders is determined by the maximum work force of said actuator piston, which is chosen constant for said common borders.

37. A combination according to claims 35 or 36, wherein said chamber is further comprising a wall which is parallel to the centre axis of said chamber.

38. A combination according to claims 35-37, wherein said chamber is further comprising a concave shaped wall.

39. A combination according to claim 38, wherein said chamber is further comprising a transition between said convex shaped wall and said parallel wall, wherein said transition may be comprising a concave shaped wall.

40. A shock absorber comprising:

a combination according to any of claims 1 to 39,

- means for engaging the piston from a position outside the chamber, wherein the engaging means have an outer position where the piston is at the first longitudinal position of the chamber, and an inner position where the piston is at the second longitudinal position.

41. A shock absorber according to claim 40, further comprising an enclosed space,

communicating with the container.

42. A shock absorber according to claim 41, wherein the enclosed space has a variable volume.

43. A shock absorber according to claim 41, wherein the enclosed space has a constant volume.

44. A shock absorber according to claim 41, wherein the enclosed space is adjustible.

45. A shock absorber according ta claims 41 - 44, wherem the container and the enclosed space form 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 of the chamber.

46. A pump for pumping a fluid, the pump comprising:

a combination according to claims 1-39,

means for engaging a second piston in a second chamber from a position outside the chamber,

- a fluid entrance connected to the second chamber and comprising a valve means, and

a fluid exit connected to the second chamber.

47. A pump for pumping a fluid, the pump comprising:

a combination according to claims 1-39,

- means for engaging a piston in the chamber 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.

48. A pump according to claim 46 or 47, wherein the engaging means have an outer position where the piston is at the first longitudinal position of the chamber, and an inner position where the piston is at the second longitudinal position of the chamber.

49. A pump according to claim 46 or 47, wherein the engaging means have an outer position where the piston is at the second longitudinal position of the chamber, and an inner position where the piston is at the first longitudinal position of the chamber.

50. The use of a piston-chamber combination according to claim 1 or 2 in a motor, specifically a car motor.

51. A motor, characterized by the fact that it comprises attached hereto a piston-chamber combination according to claim 1.

52. A motor, characterized by the fact that it comprises attached hereto a piston-chamber

combination according to claim 2.

53. A motor according to claims 1, 3 - 39, 46 - 51 wherein the crankshaft is comprising a second enclosed space, communicating at one end with an external pressure source, and at the other end with the enclosed space of said actuator piston.

54. A motor according to claim 53 wherein the crankshaft is comprising a third enclosed space, communicating the enclosed space of the actuator piston, and and at the other end communicating with a repressuration pump, which is communicating with an electric motor, said motor gets it energy from a battery which is charged by an energy source, such as solar power, or a fuel cell, such as a H₂ -fuel cell, 6r an alternator which is communicating with said main axle.

55. A motor according to claim 54, wherein said alternator is communicating with the axle of an auxiliarly power source, such as a combustion motor which is burning H₂ derived from electrolysis of conductive water, and 0₂ of the air, the water corning from a tank which can be filled up externally.

56. A motor according to claim 54, wherein the last mentioned pump is communicating with the axle of an auxiliarly power source, such as a combustion motor which is burning H₂ derived from electrolysis of conductive water, and 0₂ of the air, the water coming from a tank which can be filled up externally.

57. A motor according to claim 53, wherein the communication between the pressure source and the enclosed space of said actuator piston takes place during a part of each crankshaft turn.

58. A motor according to claim 54, wherein the communication between the enclosed space of said piston and the repressuration cascade takes place during a part of each crankshaft tarn.

59. A motor according to claims 57 and 58, wherein said communications are separated in time from each other.

60. A motor according to- claim 59, wherein said communications are performed by a T- valve, being controlled by a computer which is electrically communicating with the main axle of said motor.

61. A motor according to claim 60, wherein the pressure and/or volume of the supply channel to said T-valve is being controlled by a reduction valve, said reduction valve being controlled by a speeder.

62. A motor according to claim 61, wherein said reduction valve is communicating with a pressure storage vessel, which is communicating with a repressuration cascade of pumps, of which at least one pump is communicating with the main axel [of said crankshaft, through another crankshaft,] while at least one pump is communicating with an electric motor, said motor gets it energy from a battery which is charged by an energy source, such as solar power, or a fuel cell, such as a H₂ -fuel cell, or an alternator which is communicating with said main axle.

63. A motor according to claim 62, wherein said alternator is communicating with the axle of an auxiliarly power source, such as a combustion motor which is burning H₂ from electrolysis of conductive water, and 0₂ of the air, the water coming from a tank which can be filled up externally.

64. A motor according to claim 63, wherein the last mentioned pump is communicating with the axle of an auxiliarly power source, such as a combustion motor which is burning H₂ from electrolysis of conductive water, and 0₂ of the air, the water coming from a tank which can be filled up externally.

65. A motor according to claims 62 - 64, wherein said pumps are piston pumps or rotational pumps.

66. A motor according to claims 2 - 39, 46 - 51, wherein the enclosed space, the second enclosed space and the third enclosed space form a closed cavity.

67. A motor according to claim 66, wherein the pressure in said cavity is being controlled by a piston-chamber combination, which communicating with a bi-directional piston-chamber

combination

which is controlled by a reduction valve, which is controlled by a speeder.

68. A motor according to claims 67, wherein said bidirectional actuator piston-chamber combination is which is communicating with a pressure vessel, said vessel is communicating with a repressu- ration cascade of pumps, of which at least one is communicating with the main axel [of said crankshaft, through another crankshaft], while at least one pump is communicating with an electric motor, said motor gets it energy from a battery which is charged by an energy source, such as solar power, and/or by electricity from a fuel cell, such as a H₂ -fuel cell, and/or by an alternator which is communicating with said main axle.

69. A motor according to claim 68, wherein the last mentioned pump is communicating directly with the axle of the auxiliarly power source, such as a combustion motor which is burning H₂, derived from electrolysis of conductive water, and 0₂ from the air, the water coming from a tank which can be filled up, and when necessary from a conductive means storage tank

70. A motor according to claim 67-69, wherein the pressure in said cavity is being additionally controlled by a piston-chamber combination, which is communicating with said pressure vessel.

71. A motor according to claim 65, wherein the pressure in the closed cavity of a piston is controlled by a piston-chamber combination, which is communicating with the main axle of said motor, electronically by a computer.

72. A motor according to claim 65, wherein the pressure in the closed cavity of a piston is controlled by a piston-chamber combination, which is communicating with the main axle of said motor through a cam wheel, which is communicating with a cam shaft.

73. A motor according to claims 61 or 70 , wherein said pumps are piston pumps or rotational pumps.

74. A motor according to claims 1 -4, 6 - 73, wherein a piston is rotating around the centre axis of the chamber.

75. A motor according to claims 1 - 4, 6 - 73, wherein the chamber is rotating.

76. A motor according to claims 74 and 75, wherein the piston and the chamber are rotating.

77. A motor according to claim 74 -76, wherein the actuator piston-chamber combination is comprising at least two sub-chamber, which are comprising an actuator piston, said sub-chambers are

positoned in continuation of each other, whereby a first circular position of sub-chamber is adjacent to a second circular postion of another adjacent sub-chamber.

78. A motor according to claim 77, wherein the sub-chambers are identical.

79. A motor according to claim 78, wherein each sub-chamber is comprising an actuator piston, said pistons are identical, where each piston is positioned at a different circular position per sub-chamber, in relation to each other.

80. A motor according to claims 74-79, wherein the shape of the piston is not changing during the stroke.

81. A motor according to claims 62 or 68, wherein the pressure vessel is being pressurized by an external pressure source, through a pluggable connection.

82. A motor according to claims 54, 62 or 68, wherein the battery is being charged by an external electrical power source through a pluggabe connection.

83. A piston-chamber combination comprising an elongate chamber (70) which is bounded by an inner chamber wall (71,73,75) and comprising a piston means (76,76', 163) 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 at the first and second longitudinal positions of said chamber and at least substantially continuously differing cross-sectional areas 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 means being designed to adapt itself and said sealing means to said different cross- sectional areas of said chamber during the relative movements of said piston means from the first longitudinal position through said intermediate longitudinal positions to the second longitudinal position of said chamber,

characterized by the f ct that

the piston means (76,76', 163,189,189') comprises:

a plurality of at least substantially stiff support members (81,82,184) rotatably fastened to a common member (6,23,45,180),

said support members being provided in elastically deformable means (79), supported by - said support members, for sealing against the inner wall (71,73,75,155,156,157,158) of the chamber (70) said support members being rotatable between 10° and 40° relative to the longitudinal axis (19) of the chamber (70),

- the support members (81 , 82 , 184) are bendable .

84. A piston-chamber combination according to claim 83, wherein said piston inside or outside said

chamber to be sealingly movable relative to said chamber wall.

85. A piston-chamber combination according to claim 83, wherein the support members having a pre-determined bending force.

86. A piston-chamber combination according to claim 83, wherein the support members (81,82, 184) are rotatable so as to be at least approximately parallel to the longitudinal axis (19).

87. A piston-chamber combination according to claim 83, wherein the elastically deformable means (79) is made of Polyurethane-foam.

88. A piston-combination according to claim 87, wherein the PU-foam is comprising a Poly- urefhane Memory foam and a Polyurethane foam.

89. A piston-chamber combination according to claim 88, wherein the Polyurethane foam is comprising a major part is Polyurethane Memory foam, and a minor part Polyurethane foam.

90. A piston-chamber combination according to claims 87 - 89, wherein the Polyurethane foam is provided with a flexible impervious layer.

91. A piston-chamber combination according to claim 90, wherein the impervious layer has an unstressed production size of which the circumference is approximately the circumference of the wall of the chamber at a second longitudinal or circular position.

92. A piston-chamber combination according to claims 83 or 86, wherein the common member is attached to a crankshaft.

93. A piston-chamber combination according to claims 83 or 88, wherein the common member is attached to a piston-chamber combination, which is an external bidirectional actuator.

94. A piston-chamber combination comprising an elongate chamber (70) which is bounded by an inner chamber wall (71,73,75) and comprising a piston means (76,76', 163) 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 at the first and second longitudinal positions of said chamber and at least substantially continuously differing cross-sectional areas at intermediate longitudinal positions between the first and second longitudinal positions thereof, the cross-sectional area at the first longimdinal position being larger than the cross-sectional area at the second longitudinal position, said piston means being designed to adapt itself and said sealing means to said different cross- sectional areas of said chamber during the relative movements of said piston means from the first longitudinal position through said intermediate longitudinal positions to the second longitudinal position of said chamber,

characterized by the fact that

the piston means (49, 49') comprises:

a plurality of at least substantially stiff support members (43) rotatably fastened by an axle (44) to a piston rod (45),

said support members being supported by a sealing means (41), said sealing means being supported by spring 42, for sealing against the inner wall (71,73,75,155,156,157,158) of the chamber (70) said support members being rotatable between _! ⁰ and ° relative to the longitudinal axis (19) of the chamber (70),

a flexible impervious membrane (sheet) (40) is mounted in said sealing means (O-ring) (41),

and is positioned perpendicular to the centre axis (19) of said chamber (1),

said membrane (flexible impervious sheet) is comprising a reinforment layer,

said support members (means), said sealing means (O-ring), said flexible impervious membrane (sheet) and said (lying) spring are vulcanized on each other.

95. A piston-chamber combination according to claim 94, wherein the support members (81- ,82,184) (means) are rotatable so as to be at least approximately parallel to the longitudinal axis (19).

96. A piston-chamber combination according to claim 94, wherein said flexible reinforment layer (sheet) is comprising a spiral shaped reinforcement.

97. A piston-chamber combination according to claim 94, wherein said reinforment layer (sheet) is comprising a concentrically shaped reinforcement, positioned around the centre axis of said chamber.

98. A piston-chamber combination according to claim 94, wherein said flexible impervious membrane (sheet) having a more than 90° angle with the centre axis of said centre axis of said chamber.

99. A piston-chamber combination according to claim 98, wherein said flexible impervious membrane (sheet) is mounted on said piston rod.

100. A piston-chamber combination according to claim 98, wherein said flexible impervious membrane (sheet) is vulcanized on said piston rod.

101. A piston-chamber combination according to claims 83 or 94, wherein the common member is comprised in a piston-chamber combination.

102. A piston-chamber combination according to claim 94, wherein the flexible impervious sheet is being supported by a foam.

103. A piston-chamber combination according to claim 102, wherein said foam is being reinforced with stiff member, which are rotatably fastened to the piston rod.

104. A piston-chamber combination comprising a chamber (162,186,231) which is bounded by an inner chamber wall (156,185,238), and comprising a piston means inside said chamber to be engagingly movable relative to said chamber wall at least between a first longitudinal position and a second longitudinal position of the chamber,

said piston means comprising a container (208,208' ,217,217' ,228,228' ,258,258' , 450,450') which is elastically deformable thereby providing for different cross-sectional areas and circumferential lengths of the piston adapting the same to said different cross-sectional areas and different circumferential lengths of the chamber during the relative movements of the piston between the first and second longitudinal positions through said intermediate longitudinal positions of the chamber,

the piston means is produced to have a production-size of the container (208,208' , 217,217', 228,228' , 258,258', 450,450') in the stress-free and undeformed state thereof in which the circumferential length of the piston is approximately equivalent to the circumferential length of said chamber (162,186,231) at said second longitudinal position, the container being expandable from its production size in a direction transversally with respect to the longitudinal direction of the chamber thereby providing for an expansion of the piston from the production size thereof during the relative movements of the actuator piston from said second longitudinal position to said first longitudinal position,

the container (208,208', 217,217', 228,228', 258,258', 450, 450') being elastically deformable to provide for different cross-sectional areas and circumferential lengths of the actuator piston, characterized by the fact that

the piston means (92,92', 146,146', 168,168', 208,208', 222,222', 222") comprises an elastically deformable container comprising a deformable material (103, 103', 124,124', 136,137,173, 173', 174,174' , 205,205' ,206,206'215,215' ,219,219').

105. A piston-chamber combination according to claim 104, wherein said container in said chamber to be sealingly movable relative to said chamber wall.

106. A piston-chamber combination according to claims 104 or 105, wherein the deformable material (103, 103' , 124, 124', 136,137,173, 173', 174, 174', 205,205' , 206,206'215,

215 ',219, 219') is a fluid or a mixture of fluids, such as water, steam and/or gas, or a foam.

107. A piston-chamber combination according to claim 106, wherein the deformable material (124,124', 136,174,174',205,205',219,219') is at least substantially incompressible.

108. A piston-chamber combination according to claim 106 or 107, wherein the container is inflatable.

109. A piston-chamber combination according to claim 104 or 105, wherein the combination additionally is comprising a piston rod, the wall of the container is comprising a flexible material, which is vulcanized on said piston rod.

110. A piston-chamber combination according to claim 109, wherein the wall of the container is comprising at least a layer with a reinforcement, positioned nearest to the piston rod and vulcanized on that, and a layer without a reinforcement which is vulcanized upon said layer with a

reinforcement.

111. A piston-chamber combination according to claim 110, wherein the reinforcement strengs are laying parallel to the centre axis of said piston, and are bendable.

112. A piston-chamber combination according to claim 108 or 109, wherein the wall of the container is comprising two reinforcement layers, where the reinforcements of said laywers are crossing each other with a very small angle.

113. A piston-chamber combination according any of the claims wherein the length of a container type piston is enlarged, so that the shape of an ellipsoide shaped piston at a second longitudinal position is remaining its shape, but not its size when being on a first longitudinal position.

114. A motor according to claim 51, wherein a pressure regulator which is communicating with a pressure vessel and a third enclosed space, is communicating with a speeder.

115. A motor according to claim 51, further comprising two cylinders, wherein the third enclosed space of each cylinder are communicating with each other through the connection of the two sub-crankshafts which are comprised in the crankshaft of said motor, and the second enclosed spaces of each cylinder are communicating with each other outside said crankshaft. (Fig. 19)

116. A motor according to claim 115, wherein the crankshaft configuration of two piston- chamber combinations the connector rods are positioned 180° from each other. (Fig. 19)

117. A motor according to claim 115 and 116, further comprising more than two cylinders, wherein a second enclosed space is connected through the connection of said sub-crankshafts of the existing two cylinders, with the second enclosed space of the sub-crankshaft of the cylinder to be added. (Fig. 19)

118. A motor according to claim 52, further comprising two cylinders, wherein the 2^nd longitudinal position of one cylinder is at the same geometrical level of the 1st longitudinal position of a second cylinder, both actuator pistons are communicating with each other through a crankshaft, said crankshaft is comprising two connected sub-crankshafts, one for each actuator piston, where the connection rods to these actuator pistons are positioned 180° from each other. (Fig. 17)

119. A motor according to claim 118, further comprsing ESVT pumps for each of the

cylinders, wherein said pumps are combined for said two cylinders into one pump, through communication of the enclosed space of one of the actuator pistons with the enclosed space of the other of the actuator pistons, said enclosed spaces being comprised in said crankshaft, said enclosed spaces are communicating with each other at the connection point of said sub-crankshafts. (Fig. 17)

120. A motor accordung to claim 119, further comprising valves, which are opening and closing the connection between said ESVT-pump and said second or third enclosed spaces, while each connection has a check valve or check valve function, said valves are controlled by either the pressure of said ESVT-pump and/or by tappets, said tappets are communicating with a camshaft, which is communicating with the main axle of an auxilliarly motor. (Fig. 17)

121. A motor according to claims 118 - 120, further comprising more than two cylinders, where each added cylinder is communicating through the enclosed spaces of the connected sub- crankshafts of the existing sub-crankshafts. (Fig. 17)

122. A motor according to claim 52, further comprising two cylinders, wherein the 1st longitudinal position of one cylinder is at the same geometrical level of the 1st longitudinal position of a second cylinder, both actuator pistons are communicating with each other through a crankshaft, said crankshaft is comprising two connected sub-crankshafts, one for each actuator piston, where the connection rods to these actuator pistons are positioned 0° from each other. (Fig. 18)

123. A motor according to claim 122, further comprsing ESVT pumps for each of the cylinders, wherein said pumps are combined for said two cylinders into one pump, through communication of the enclosed space of one of the actuator pistons with the enclosed space of the other of the actuator pistons, said enclosed spaces being comprised in said crankshaft, said enclosed spaces are communicating with each other at the connection point of said sub-crankshafts. (Fig. 18)

124. A motor accordung to claim 123, further comprising valves, which are opening and closing the connection between said ESVT-pump and said second or third enclosed spaces, while each connection has a check valve or check valve function, said valves are controlled by either the pressure of said ESVT-pump and/or by tappets, said tappets are communicating with a camshaft, which is communicating with the main axle of an auxilliarly motor. (Fig. 18)

125. A motor according to claims 122 - 124, further comprising more than two cylinders, where the enclosed space(s) of each added (couple) cylinder(s) is(are) separated through a filler in the connection with said existing sub-crankshafts, and where the power strokes of the added cylinders are simultaneously the return strokes of the existing cylinders. (Fig. 18)

126. A motor according to claim 52, further comprising 2 cylinders wherein the connection rods are in a position of 180° from each other, while the chambers have an identical geometrical position of their 1^st and 2^ηΛ longitudinal positions. (Fig. 18)

127. A motor according to claims 115 - 126, wherein the piston-chamber combinations for each of the enclosed spaces in a sub-crankshaft, which are changing the speed/pressure in a cylinder are communicating with each other through the electric pressure regulator of the 2- way actuators, which is moving the piston rod of each of said piston-chamber combinations, and is communicating with the external speeder.

128. A motor according to claims 115-127, wherein the piston rods of the pumps, pressurizing the fluid in said pistons, are being powered by a 2 way actuator piston powered by a battery, which is powered by an auxilliarly power source.

129. A motor according to claims 115-128, wherein the piston rods of the pumps, pressurizing the fluid in said pistons, are being powered by a 2 way actuator piston powered by a battery, which is powered by an auxilliarly power source.

130. A motor according to claims 115-129, wherein the piston rods of the pumps, pressurizing the fluid in said pistons, are being powered by a 2 way actuator piston powered by a crankshaft, which is powered by an auxilliarly power source.-

131. A motor according to claims 115-130, wherein the piston rods of the pumps, pressurizing the fluid in said pistons, are being powered by a 2 way actuator piston powered by a cramshaft, which is powered by an auxilliarly power source.

132. A motor according to claim 52, which is comprising a circular chamber and a actuator

piston, wherein the piston rod is sealingly movable in a cylinder, and the enclosed space inside said piston rod is communicating with pressure controller, which is communicating with a remotely positioned speeder, while the size of the enclosed space is regulated by a pump with a conical chamber, of which end is running over a cam profile, said cam profile is driven by an auxilliarly electric motor which is turning said cam, and turning independantly of said motor around the same main motor axle.

133. A motor according to claim 132, wherein said actuator piston having a wall a reinforcement,

said wall being mounted on an end fixed on said piston rod, and on a movable end, which can sealingly slide on said piston rod.

134. A piston-chamber combination comprising an elongate chamber (70) which is bounded by an inner chamber wall (71,73,75) and comprising a piston means (76,76' ,163) 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 at the first and second longitudinal positions of said chamber and at least substantially continuously differing cross-sectional areas 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 means being designed to adapt itself and said sealing means to said different cross- sectional areas of said chamber during the relative movements of said piston means from the first longitudinal position through said intermediate longitudinal positions to the second longitudinal position of said chamber, the piston means (1300) is comprising:

a plurality of at reinforcement pins (1302,1303,1304) rotatably fastened to a holder- plate (1307) which is comprised by a holder (1308),

said reinforcement pins being provided in elastically flexible foam, supported by

said reinforcement pins, for sealing against the inner wall (XXXX) of the chamber (70) said reinforcement pins being rotatable between 0° and 40° relative to the longitudinal axis (1319) of the chamber (70),

an impervious layer 1305, which is elastically flexible,

characterized by the fact that

- me reinforcement pins are made of metal,

said holder plate is made of metal, and is comprising small closed , rounded off end holes

(1329, 1330, 1331) in more than one row (1326,1327,1328),

said reinforcement pins are being fastened by magnetic force to said holder plate.

135. A piston-chamber combination comprising an elongate chamber which is bounded by an inner chamber wall and comprising a piston means 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 at the first and second

longitudinal positions of said chamber and at least substantially continuously differing cross-sectional areas 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 means being designed to adapt itself and said sealing means to said different cross- sectional areas of said chamber during the relative movements of said piston means from the first longimdinal position through said intermediate longitudinal positions to the second longitudinal position of said chamber, wherein - the piston means comprises an elastically deformable container comprising a deformable material, the deformable material is a fluid or a mixture of fluids, such as water, steam and/or gas, or a foam, characterized by the fact that

the wall of said container is comprising a separate wall part (2106, 2112, 2113, 2123, 2133, 2142, 2143, 2207, 22xx, 22xx", 2244, 2244"; 2145, 2199, 2238), said separate wall part has a bigger circumference than the rest of the wall of said container, and is comprising the contact area with the wall of said chamber

136 A piston-chamber combination comprising an elongate chamber (70) which is bounded by an inner chamber wall (71,73,75) and comprising a piston means (76,76', 163) 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 at the first and second longitudinal positions of said chamber and at least substantially continuously differing cross-sectional areas at intermediate longitudinal positions between the first and second longitudinal positions thereof, the cross-sectional area at the first longi dinal position being larger than the cross-sectional area at the second longitudinal position,

a plurality of reinforcement pins (1352,1353,1354) rotatably fastened to a holder plate (1358) which is comprised by a holder (1359),

said reinforcement pins being provided in an elastically flexible foam, supported by said reinforcement pins, for sealing against the inner wall ( XXX) of the chamber (XXXX) said reinforcement pins being rotatable between 0° and 40° relative to the longitudinal axis (1319) of the chamber (70),

an impervious layer 1305, which is elastically flexible,

characterized by the fact that

- the reinforcement pins are made of a plastic, having sphere shaped ends (1355, 1356, 1357), said holder plate is comprising small closed , rounded off sphere cavities (1360, 1361, 1362) in more than one row (1326,1327,1328),

said sphere shaped ends fit into said rounded off sphere caivities,

said holder plate is further comprising openings (1363, 1364,1365) for guiding said

reinforcement pins.

137. A motor according to any of the claims 1-136, further comprising a circular chamber (4001) in which

a piston (4000) is moving around the centre point (3995) of said chamber, a connecting rod (4003) having a centre axis (4008), and an axle (4002) having a centre axis, wherein said piston (4000) is connected to said axle (4002) by a connecting rod (4003),

138. A motor according to claim 137, wherein the connecting rod (4003) is positioned perpendicular to said axle (4002), the centre axis (4008) of the connecting rod (4003) and the centre axis of axle (4002) are going through the center point (3995).

139. A motor according to claim 137 or 138, further comprising an extension rod (4020), wherein said connecting rod (4003) is connected through an extension rod (4020) to said piston (4000), the distance (Ι, ) between the crossing point (3990) of the centre axis (4008) of the connecting rod (4003) and the centre axis (3996) of the chamber (4001) and the end (3991) of the extension rod (4020) is variable.

140. A motor according to claim 137 or 138, further comprising a pressure management system, and a hub which is mounting said connecting rod onto said axle, wherein said piston (4000) is communicating with said pressure management system, through a channel 4004 of said axle (4002), a channel (4006) in the wall of said axle (4002), a channel (4006') in said hub (4009), a channel (4005) of said connecting rod (4003), and a channel (4025) in said extension (4020) to the space (4026) of said piston (4000), through a channel (4027) in the extension rod (4020).

141. A motor according to claims 137-140. wherein said hub (4009) is comprising a contra weight (3994).

142. A motor according to claims 137 - 141, wherein said axle (4002) is slidingly mounted onto said connecting rod (4003) by a hub (4009), which is comprising teeth (4007) fitting into grooves (4007') of said axle (4002).

143. A motor according to claim 142, wherein the communication between the inside

(4026) of said piston (4000) and said pressure management system through the channels (4025), (4005), (4006'), (4006) and (4008) of the extension rod (4020), the connecting rod (4003), the wall of the hub (4009), the wall of the axle (4002), and the axle (4002), respectively, is constant.

144. A motor according to claims 137 - 143, wherein the axle (4032) is connected to the connecting rod (4033) by a hub (4038) which is comprising teeth (4007) fitting into grooves (4007') of said axle (4002), and additionally wherein said circular chamber 4001 is connected through spokes (4034) mounted on a hub. (4035) to said axle (4002), where in between said hub (4035) and said axle (4002) a bearing (4039) is positioned, wherein between said hub (4038) which is connected to the connecting rod 4033, and said axle (4032), having a channel (4043) which is constantly communicating with said channel (4046) of said connecting rod (4033) through said channel (4045) in the wall of said hub (4038), and with the channel (4034) of said axle (4032) through said the channel (4044) in the wall of said axle (4032). (Fig. 91B)

145. A motor according to claims 137-144, wherein the bearing (5100) is both a part of the hub (5101), which is assembling the (piston through the) connecting rod (5102) to the axle (5103), and part of the hub 5104, which is connecting the spokes (5105) (suspending the chamber) to the axle (5103), said connecting rod (5102) having a channel (5109) and the axle (5103) having a channel (5114), the communication between said channels is interrupted by said bearing (5100). (Figs. 91C,D).

146. A motor according to claiml44 or 145, wherein said axle (4002) is comprising an additional channel 4041, by a reduced diameter of the part 4046 of said axle 4040, and is positioned near the channel 4042 in the wall of said part 4046.

147. A motor according to claiml46, wherein the communication between the channel (4035) of said connecting rod (4003) and the channel (4034) of said axle (4032) is constant.

148. A motor according to claims 137-147, further comprising 3 circular chambers with pistons moving therein, a housing, a hub, a motor axle and a gearbox, wherein said chambers (4092) are positioned parallel to each other and interconnected by said housing (4095), and wherein said pistons ((4091) are assembled onto said motor axle (4094) by a hub (5005), the motor axle (4094) is communicating directly with the axle (5004) of the gearbox (4093), comprising a driveshaft axle

(5000) and the channel (5002) within said motor axle (4094) is communicating with the enclosed space (5003) of each piston (4091), and communicating with the pressure management system

(5001) .

149. A motor according to claims 137-147, further comprising 3 circular chambers with pistons moving therein, a housing plate, a motor axle, and a gear with variable pitching wheels and belts, wherein said chambers are connected to each other by said housing plate (5017), said pistons (5011) are connected to said motor axle (5013) by a connecting rod (50xx) and a hub (5019), a pitching wheel (5014) is positioned on each of the two sides of said motor (5010), and where said variable pitching wheels (5014) are connected to comparable wheels (5015) by a belt (5021), mounted on a wheel axle 5016 of a vehicle, said variable pitching wheels (5014, 5015; 5014', 5015') may be pitched low and high., wherein the distance x between the wheel axles 5016 of said pitching wheels (5014, 5015; 5014', 5015') remains unchanged.

150. A motor according to claims 137-147, further comprising 3 rotating circular chambers, a central axle, hubs, corners on each side of a chamber, an external gearbox and a pressure management system, wherein the corners (5023, 5023') are connected to each chamber (5021), the central axle (5022) is comprising a bearing (5033) and an inner axle (5032), said inner axle (5032) is comprising a channel (5037) communicating with the internal space (5038) of each piston (5025) through a channel (5039) of a connecting rod and a hub (5034), said central axle (5022) is comprising parts (5022') outside each hub (5034) of each piston (5025) and further comprising a bearing (5033), which is comprising parts (5033'), corresponding to the parts of said central axis (5022), and the hubs 5034 are mounted onto the inner axle 5032, said central axis 5022 is communicating with an external gearbox (5024) , while each chamber (5021) is comprising a ring (5026) which is positioned farthest from the central axis (5022).

151. A motor according to any of claims 1 - 150, further comprising a pressure management system, and a vehicle, amoung others two parallel positioned wheels, mounted on each wheel a motor, said wheels are capable of turning around a center, wherein said pressure management system (1983) for each of the motors (1970, 1971) is controlled by the turning angles a and b, resp., where angle a > b, through the signals (1981, 1982), which are being transferred to a computer (1983), are being worked in and resulting in control signals (1984, 1985), which are being transferered to each of said motors (1970,1971).