DE3333376A1 - FLYING FORCE EXPANSION METHOD AND PISTON EXPANSION DEVICE - Google Patents

Description

Centrifugal expansion method and piston expansion

sion facility

This invention relates to a method and a rubbing t.;:; Ncr zwva extraction of heat and / or mechanical _ "

ünergi-Ξ from a pressurized gas, thereby, that nuTiri this in a piston and cylinder unit expands, in which the cylinder with the power output shaft connected and rotatable therewith.

Literally thousands of patents have dealt with the problem, either heat or mechanical energy effectively withdrawing from a pressurized gas. In the broadest sense, an internal combustion engine, which interacts with a back and forth

movable piston and cylinder, a device for extracting mechanical energy from a pressurized gas produced by the combustion of a suitable fuel in the op cylinder chamber. Air conditioning and / or air cooling devices have been known for a long time, the expansion of a cooling gas being effected by the fact that the gas is passed in compressed form into a cylinder chamber ? X into which a piston is introduced.

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and is moved. The movement of the piston out of its smallest volume position in the cylinder chamber in its position of greatest volume creates an expansion and thus also a seal of the compressed gas, and the cooled gas can be used for air conditioning and other cooling purposes be used. If the piston is connected to a conventional crankshaft, then a mechanical one can be used Energy can be derived from the gas expansion stroke of the piston in order to efficiently use energy to improve the piston expansion device. ■

In all such prior art arrangements, the reciprocating piston is common connected to a crankshaft by a connecting rod, and especially when several such pistons are required to achieve the desired. To generate power or mechanical energy or the desired cooled, expanded gas. The crankshaft and the connecting rods are expensive items to be made, assembled, and maintained in good, bet. It has been so far no device provided in the state of the art, which causes the expansion of the compressed gas in a cylinder chamber, while the cylinder chamber is fixedly attached to a rotatable body and the mechanical output of the expanded Gas is generated by the counterforce on the cylinder. Not a prior art facility eliminates the need for any mechanical connection between the piston and the rotating body for power transmission purposes, and the piston is moved inward and then relative to the rotating axis by the expanding gas moved outward primarily by centrifugal force generated by the rotating body that wearing the cylinder.

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The invention provides a method and a device for extracting heat and / or mechanical energy from a pressurized gas, with a pressurized gas generated by a combustible fuel is, with one or more cylinders mounted for rotation about the axis of a work shaft are. The fluid pressure chamber defined by the cylinder extends from a point which far from the axis of rotation, to a point close to this axis or passes through this axis if the outer shape is changed, the longitudinal axis of the Strör.ur-gsirdt-teldruckkamrnör is not radial, however be ;; cgi: -λ arranged on the axis of rotation, but points eir.ea -V.ui-jren- end section, which is essentially not rad. '. al is arranged. In the preferred embodiments of the invention is the end wall of the cylinder in a radial plane with respect to the axis of rotation the ararbeitsveil arranged.

A piston is in each cylinder for a sliding and sealing movement attached to it. The piston is in a position on the very outside of the cylinder in the first place Line moved by the centrifugal force generated by the rotation of the cylinder around the axis of rotation. A starter rotor is connected to the working shaft to initially produce such a centrifugal force. Of the Piston is moved inward by the expansion of a charge of compressed gas at the other end of the cylinder either by connection via a valve or by burning a combustible fuel mixture is produced. The piston is moved from its innermost position primarily by centrifugal force returned, so that the requirement for any ".liche Crankshaft connection of the piston with the output shaft is unnecessary for power transmission purposes. The reaction force of the expanding gas will against the end wall of the fluid pressure chamber: exercised and generate: a torque on the rotating cylinder

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he raises a constant moment arm with respect to the Axis of rotation. This reaction force provides the mechanical Power output. = from the expanding gas.

Since the reciprocating movement of the piston is not mechanically assigned to the rotation of the working shaft, must a special valve arrangement may be provided to close the inlet of the filling of pressurized gas or combustible fuel to the other end of a fluid pressure chamber and the subsequent outlet of the expanded gas from the fluid pressure chamber to effect. In a modified embodiment of the invention, such a valve arrangement caused by an oscillating sleeve which is arranged around the working shaft and through a connecting rod is connected to the piston. In an ant'iäreri embodiment of the invention, the Valve control effected by the piston engaging a valve stem on the other End of the fluid pressure chamber is attached and with. the.·; Piston is engaged when out bowegt is. In still other embodiments of the invention, the location of the piston detected by electronic or electromagnetic measuring devices arranged around the cylinder and generate a signal when the piston passes the special measuring device. The output signals The control signals are fed from such measuring devices to a logic circuit generated to solenoid operated. Actuate intake and exhaust valves attached to the cylinders are. When the Pliehkraft piston expander is used specifically as an internal combustion engine, then the logic circuit also generates a Ignition signal sent to a spark plug or similar device that ignites combustible fuel must be in the other end of the fluid pressure chamber attached by the rotating

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q «Ι Λ - ■ * ή -

4 f. ** * * f ^Λ

Cylinder is delimited.

If several pistons and cylinders are attached to a single rotating body, one must in turn Means may be provided to coordinate the reciprocating movements of the pistons in order to maintain the dynamic compensation of the rotating assembly. In another embodiment of the invention such coordination is carried out by a mechanical, alternate connection of the piston through the BenÜT-i-U'- : eir; or single: valve sleeve sr and connecting pliers causes which extend from this to the individual pistons. In yet another embodiment of the invention ^ irci. coordination electronically through use a "UKD" circuit which requires that all pistons reach the same point before a special valve is actuated, for example the '' inlet valve for the flow inlet! pressure chamber. The inlet valves for the flow / kittal pressure chambersKn are actuated together when all pistons are in their outermost position in the flow pressure chamber achieved.

If there are electronic or electromagnetic measuring devices used to measure the location of the pistons in the respective cylinders, then there is no requirement for any mechanical connection between the cylinders. As a result, training can of the fluid pressure chamber, starting from the conventional cylindrical shape, to a Graze chambers with a circular cross-section modified, which has an arcuate longitudinal axis to effectively increasing the length of the path of travel of the pistons in the respective cylinders without reducing the overall diameter to increase the overall arrangement. Thus, the fluid pressure chamber can be in the form of a Assume an arc or a spiral whose long axes lie in the same plane. The fluid

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pressure chamber can also comprise a helical spiral. In a preferred, modified embodiment of the invention, the fluid pressure carnmor have an S-shaped design, which extends from a point remote from the cylinder over an arc extends away to run through the axis of rotation or in the vicinity thereof and then over a To extend arches with reverse curvature to a second, remote location. In this training the required inlet and outlet valves are respectively at the far ends of the special S-shaped cylinder attached. For internal combustion engines is also a spark plug or another. Kind of a sin device at each of the far ends appropriate. The inlet and outlet valves and the spark plugs are operated electronically or electromagnetic piston position sensors controlled - slide with mutual distance along the S-shaped cylinder are arranged.

The operator will recognize that using a "free" piston that is movable in a cylinder that rotates about a working shaft axis, a substantial simplification of the structure of either one Is expansion device for air conditioning purposes or for a gas pressure operated engine. Of the The fact that a crankshaft is unnecessary significantly reduces the cost of the arrangement and simultaneously allows the use of longitudinal

direction curved cylinders, which significantly increase the efficiency of the gas expansion work.

Other objects and advantages of the invention will become apparent to those skilled in the art from the following detailed description apparent in connection with the attached The drawing is to be consulted.

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In the drawing is:

Fig. 1 is a schematic, partially sectioned side view a centrifugal piston expander embodying this invention and

is designed to effect the cooling of an air flow,
Fig. 2 is a partially sectioned side view of the

Fig. 1,
XO Fic ;. Figure 3 is a partial sectional view of one end

one of the cylinder elements of FIG. 1, FIG. 4 is a schematic, partially sectioned view a modified gas cooler using this invention and timed Valves used by the rela

the lower positions of pistons and cylinders are actuated,

Fig. 5 is a view of a section of the Ventileinriehtung on an enlarged scale, which in rig. 4 used Χ3ΐΐ,

6 is an enlarged view of a section

Scale made in the plane 6-6 of FIG became,

Fig. 7 is a schematic, partially sectioned view a room cooling device for one

open cycle that the centrifugal piston expander used this invention,

8 shows a schematic, partially sectioned view of a centrifugal piston expansion device,

constructed in accordance with this invention primarily for the purpose of withdrawing mechanical energy a pressurized gas source,

Fig. 9 is a view of a section taken along the plane 9-9 in Fig. 8;

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-Hi·

J- Fig. 10 is a view of a section on an enlarged scale

Scale along the plane 10-10 in Fig. 8, Fig. 11 is a partially sectioned side view of a Centrifugal piston expander embodying this invention and for the purpose It was built primarily to act as a room air cooling device, with the cooling fluid in a closed one Cycle revolves, FIG. 12 is a partially sectioned side view

a centrifugal expansion piston means, this invention is embodied and configured to act as a room-air cooling means with air being used as coolant fluid in a ¹ ^ open cycle,

13 shows the schematic view of a modified one Apparatus embodying this invention and utilizing cylinder members extending in the longitudinal direction curved fluid pressure chambers

"_

identify,

14 shows a schematic view of a further, modified one Device embodying this invention and curved longitudinally Uses fluid pressure chambers that have generally radially disposed end walls,

15 shows a schematic perspective view of a device which shows a further, modified embodiment embodied of this invention, the fluid pressure chambers having a spiral Forms a path that extends more than 3 60 ° around the axis of rotation,

Fig. 16 is a schematic perspective view of an apparatus which is another modified one

Embodiment of this invention is where 35

a longitudinally curved fluid

pressure chamber forms a helical, spiral path, and with the ends of each Pressure chamber both axial and radial

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ORIGINAL INSPECTED

Have a distance from one another;

Fig. 17 is an enlarged view of a section through a spherical piston λ used in a centrifugal piston expander is,

13 is an enlarged view of a section of an ellipsoidal piston which can be used in a centrifugal piston expansion direction,
IQ- FL-; ~ .9 ej - ^. I schematic side view of another

Apparatus embodying this invention, _{Fig 3} , 20 is a view of a section taken along plane 20-20 of Fig. 19, Fig. 21 is an enlargement of a partial section showing IcIr-gs of plane 21-21 of Fig. 19. 19 made

WUres,
22 is a schematic circuit diagram showing a

19 illustrates control mode of operation for the device of FIG.

23 is a schematic circuit diagram / the other 19 illustrates control mode of operation for the device of FIG.

24 shows a schematic / partially sectioned view, which the application of the facility. 19 to 21 for an air conditioning system Figure 25 is a schematic, partially sectioned View of the device of FIGS. 19 to 21

is used in a refrigeration system with open cycle SO,

26 is a partially sectioned view of a modified one Form of device embodying this invention and cylinder members used that have arcuate longitudinal axes,

27 is a partial sectional view, on an enlarged scale, of a modified cylinder for a device that makes this invention

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body, with solenoid-controlled intake

and exhaust valves,
FIG. 23 is a schematic view, partially in section, of a closed cycle air conditioner including the cylinders of FIG. 27;

29 is a partial sectional schematic view of an open cycle air cooling system which comprises the cylinder elements of FIG. 27, FIG. 30 is a schematic circuit diagram showing a Control mode for inlet and outlet

represents the release valves of the modified embodiments of Figs. 28 and 29,

31 and a view of a section on an enlarged scale

& .Lab, which builds an oval-shaped flask— elements represents that. Applicable to cylinders

is, the formation of which is curved in the longitudinal direction,
37 shows a view of a section on an enlarged scale

Mabstab, which has a different piston design represents which can be used for cylinders,

which are curved in the longitudinal direction,
Fig. 33 is a schematic view of a device embodying this invention and a single Sylinderelement used which forms an elongated S-shaped fluid pressure chamber _r
34 is a view of a section on an enlarged scale.

Scale of the free piston used in Fig. 33

Fig. 3 5 is a diagram scheinatiscb.es _/ illustrating the control circuit which is used during operation of the device of FIG. 33,

36 is a schematic perspective view illustrating the use of the device of FIG. 3 as a

Air conditioning represents

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37 shows a schematic perspective view of a cooling device open cycle embodying the device of Fig. 33,

38 is a schematic view of a modified form of an S-shaped flow beam pressure

chamber, and

Fig. 3? J is a schematic view illustrating the use represents three S-shaped fluid pressure chambers attached to a single, rotating Bodies are attached.

Reference is now made to Figures 1 to 3; there isv. one. Air cooling device 1 schematically ge? ii.ig ^ _f the one centrifugal piston expansion device varvsnda ··:., which embodies this invention. Such a device comprises a hollow shaft 2 which is rotated by a suitable motor (not shown). A carrier 10 is. attached to the hollow shaft 2 for common rotation. The carrier 10 can have two axially spaced, cruciform plates 11 and 12 which are each fastened to the shaft 2 for common rotation by means of bushes 13. The plates 11 and 12 of the carrier 10 are axially spaced apart by several spacer rods 15.

hold, which are each fastened by means of screws 16, In each of the four corners of the cross-shaped plates 11 and 12 there is a cylinder and piston element 20 pivotally fastened for example by means of screws 21. Those skilled in the art will recognize that the number of such piston and

Cylinder learners that were used, one thing is the free choice, as long as the respective piston and cylinder elements 20 with the same circumferential distance are arranged around the axis of rotation of the housing 10 in order to keep the arrangement dynamically balanced.

As best shown in Fig. 2, each piston and cylinder member 20 includes a cylinder 21, the a'.strömungsmi-i teldruckkammer 23 forms within

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-sa which a piston 22 is movable to and fro. The path of the reciprocating movement of each piston 22 takes place along that line which has a radial distance from the axis of rotation of the carrier 10, so that the centrifugal force normally pushes each piston 22 into a radially outward position in relation to the cooperating cylinder element 21 and thus the volume of the Fluid pressure chamber 23 to a minimum Ktr.? decreased. Each piston 22 is connected in a conventional manner by means of a connecting rod 24 to the end of a connecting rod 25. The cranks 25 are in turn rigidly attached to a hub 26 which is attached to the hollow shaft 2 for free movement. It should be particularly noted that the reciprocating motion of the piston 22 is in no way linked to the rotational movement of the working hollow shaft 2 beyond the fact that the rotational movement of the pistons 20 is the rotational shaft of the work swell ε 2 above The outwardly directed centrifugal force mentioned is generated which acts on each piston 22.

A compressor 30 is attached to the shaft 2. The compressor 30 can be any conventional form of one Rotary compressor have, with two relative to, -

2ö single rotatable components, with the exception that the compressor component 31, which is normally the Contains outlet and inlet fluid channels, is rotatable together with the shaft 2, while the "" other component of the compressor 32 is fixedly attached, as shown schematically at point 3 2a is. As will be described later, the inlet fluid for the compressor 30 is made of one Opening (not shown) fed into the hollow bore 2a of the hollow shaft 2. The outlet for pressure

^u Fluid from the compressor 30 is passed on through a plurality of pipe couplings 33 and lines 34 to valve heads 35, which are each arranged at the outer end of each piston and cylinder element 20

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-53 -

are. . ^ °

As best shown in Figure 3, each valve head 35 includes an annular block 36 defining a central bore 36a and an enlarged chamber 36b in communication with one such bore. Eir. Vc;, v "\. Isitz 37 is at the connecting stalls of Mir L ^ -I :. : ': ra: -g 36a and the enlarged chamber 36b provided - and a stem valve 38 cooperates with the valve ;: 17, whereby it is normally urged by a strong spring 39 into its closed position in which it rests. The spring 39 holds ä'cs valve 38 under operating conditions with maximum stroe ^ iurigäriittaldruck in the chamber 23 in the closed state,

Dr.'s switching valve 38 is provided with a shaft 38a; which is located in the interior of the fluid pressure chamber 23 extends and stands with -'der outer surface 22c'i des -iolbens 22 engaged when this piston is its reaches the outermost position in which he abuts against an inner shoulder 21a which is formed within the cylinder 21. In such a the valve head becomes the outer end position 38b of stem valve 38 out of engagement with the valve seat 37 lifted. Thus, pressurized fluid, supplied from compressor 30 through line 34 is released to the pressurized fluid chambers 23 to enter and exert a force on the outer surface 22a of the piston 22, to first stop the outward movement of the piston 22 and then to close that piston force yourself against the centrifugal force Vorbc-l: astung that

holds it in such an outer ¹ end position to move inwards.

Once the centrifugal force of the fluid pressure within of the fluid pressure chambers 23 overcomes the preloading centrifugal force on the pistons 22, begin the pistons 22 to move inwardly against the axis of the rotating power shaft 2 and thus to expand the pressurized gas that is in the fluid ^ DruckLararnem 23 is included. After each flask 22 has begun its Eirxwart movement, the corresponding one sits Valve 38 on the valve 37 by the action of the spring 39, and the pressurized gas filling is then enclosed within the fluid pressure chamber 23. Such a gas charge continues to expand and push piston 22 inwardly until he rait a second stop shoulder 21b into engagement occurs - which is provided on the cylinder 21. Such Inv; artic movement of the piston 22 generates an angle belt u the hub 26 carrying the cranks.

In accordance with the embodiment of this invention. 1 to 3, the expanded gas contained in the Druckströmungsmitteikäüimer 23, at the end of the inward stroke of the piston 22 through the valve opening of the piston 22 when exposing a plurality of circumferentially spaced outlet openings en 2.1c which are provided in the walls of the cylinder 21 are drained. A ring line 27 surrounds the outlet openings 21c and guides the expanded and thus cooled gas filling through a line 28 to the inlet of a heat exchanger 40, which is attached around the power shaft 2 and can be rotated together with it.

The heat exchanger 4Ό comprises a first end plate portion 41 which the ends of the fluid lines 28 records. In the immediate vicinity of the end plate 41, a collecting line 4 2 is attached, which is a bracket for several, circumferentially spaced,

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»· *
a η * «
• * • S * (ο ■ * »■
K * i ^ Λ »· η * 6 »· <» » »«

cLXially extending tubes 43 forms, which with their opposite ends are mounted in a manifold 44 which is generally similar to the manifold 42 is. A second end plate 45 is attached to the second manifold 44. Annular chambers 41a and 45ct are each between the end plate 41 and the manifold 42 'and the end plate 45 and the manifold 44 formed :. The chamber 45 a is connected to the bore 2a of the hollow shaft through radial openings 46 and permits it is thus the reheated gas, through the bore 2a eier hollow shaft 2 to the inlet (not shown) of the compressor 3 0 to flow.

To use the device described as a device for cooling or conditioning air, all that is required is a suitable line s guide and a fan to provide a Strom '- »arir.sr air laterally across the rotating Heat transfer tubes 43 to move. Such traditional pipe routing is not shown, but rather the flow of the loofah to be cooled was schematic denoted by arrows in FIG.

The operation of the device described above will be readily apparent to those skilled in the art. A flow from a suitable cold fluid is formed in a closed circuit through the device described. It begins with the output connections 33 of the compressor 3 0; such flow extends to valve heads 35 provided at the outer ends of each piston and cylinder assembly 20. When the shaft valve 38 is raised up to its open position by the piston 22, v / hen this- has arrived at its radially outermost end position °, then a charge of compressed gas, is introduced into the pressurized fluid chamber 23 formed within a jaden cylinder 21st Such a pressurized gas filling causes the axial

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bearing of the piston 22 to a radially inner one Position with respect to the axis of rotation of the working shaft 2, and zv / ar against the counteraction of the centrifugal force caused by the rotation of the piston and cylinder assemblies 20 is applied around this axis. The pistons 22 move inwardly as a result of the fact that they by connecting rods or connecting rods 24 and the cranks 25 are connected to one another, which are attached to the crank support sleeve 26. Thus the rotating one remains Arrangement always dynamically balanced.

When that piston 22 arrives at its innermost position, which is determined by the stop shoulder 21b, then are exposed ice outlet openings 21c and that expanded, cooled gas is released through the ring manifold 27 and the lines 28 to the inlet side of the Wärinea ^ Btausehars 40 promoted. The suction that exerted by the compressor 30 assists this ..:; Gitsba movement. The expanded, cooled gas passes through the heat transfer tubes 43 of the heat exchanger 40, extracts heat from the room air flowing through it and is heated in the process. The heated gas is discharged through the outlet openings 46 into the ' Bore 2a of the working hollow shaft 2 and then introduced into the flow medium inlet of the compressor 30.

The special advantage of the system described above is that during the expansion movement each piston 22 by the pressurized gas filling the reaction

° ® tion force of the expanding gas is exerted on the outer end of the cylinder assemblies 20, and that this force takes place in one direction in order to support the rotation of the working shaft 2. Thus, the energy required to operate this

^ ° System as a result of the extraction of mechanical energy can be reduced from the expansion force of the compressed gas.

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ti * *

More importantly, the successful operation of such a system does not require the use of a refrigerant such as Preon, although such a fluid could, if desired, be used to effect a phase transition from gas .-ig to liquid to gaseous A considerable cooling effect can be used by the use of ordinary air as the refrigerant, and therefore the term "refrigerant" in d; r- ₄ iu :: ■; .. ■ should smell may include any gas, including air, but preferably a gas that is non-eciotic and will not have harmful effects on the environment if it leaks into the ambient air as a result of interference.

The Facliiv.i-nn recognizes that the facility described above only a certain range of temperature reduction of the refrigerant gas, which is mainly determined by the extent to which the gas energy is expanded.

If the purpose of the device is to cool the room, and the range of temperature reduction is in the order of 16.7 K (SQ ¹ F), then obviously the temperature of the compressed gas - which in the multitude of piston- and cylinder elements 20 entering, ^{do not exceed 38 ° C (100 1} F) or less to achieve an effective level of room cooling.

It can also be seen that the action of the compressor in compressing the reheated gas is simultaneous the temperature of the gas increases. Accordingly, in most cases it will be necessary to use the compressor 30 and the drive motor for the output shaft 2 in turn to be installed in a separate room or in a chamber ° which is separate from that chamber, which is to be cooled, through a suitable wall made of heat-insulating material. Since the piston and rotating cylinder elements 20 is one such wall

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Conveniently located between the rotating support 10 and the heat exchanger 40 arranged, as shown schematically is denoted by the reference number 5 in FIG.

It may also be necessary to send the compressed gas exiting the compressor 30 through a heat exchanger-like cooling device, and this device should be on that side of the heat-insulating barrier 5 that faces away from the heat exchanger 40 - the fan (not shown ) for any such ^3rd heat exchanger, if necessary, can, however, be driven by the working shaft 2.

Bs will only. Reference is made to Fig. 4, in which like E: '; and g marks indicate parts which correspond to parts previously described; do: "~ t." st. Another Äusführungsbeispiel this Errir plication shown which uses clock-controlled valves s by the Wech selb ewegung the crank: be · bearing hub 26 is operated _r to not only the supply of pressurized fluid to the Druckströnuiricjsnittelkammern 23 of the piston = and Zylindereleraente 20 to but also to control the outlet of the cool expanded gas from the pressurized fluid channels 23 during the backward outward stroke or stroke of the piston 22. While only two piston and cylinder groups 20 are shown in detail in FIG. 4, attention is drawn to it

^ O pointed out that there are more than two such units

. normally used, but the additional units are not shown to enable that the drawings clearly show the modified valve arrangement.

At the end of the hub 26 carrying the cranks next to the support wall 11, a radial flange 26a is provided. An annular cam plate 50 is on the hub

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flange 26a fastened by means of screws 52. The cam or control plate 50 is provided with an axially protruding Control projection 5 0a provided.

An inlet control valve block 53 is attached to the outer surface of the plate 11 of the rotating support 10. The 'v = r: cilblock 53 surrounds a valve chamber 54 (Fig. 5), The «Vov -'- iikariinor 54 forms a valve seat 54a with the. ei>; Shaft valve 54b cooperates. The shaft valve 54b is normally in its sealing position with respect to the valve seat 54a by a spring 54c pressed. A stem portion 54d of stem valve 5-jb protrudes through a suitable opening in the valve block 53 unä in the side wall 11 of the carrier 10 through, ui: i to come into single grip with the control projection 50a, which is provided on the cam plate 50. Lines 34 / diy extend from the discharge site of the compressor 3 0 aas are each connected to valve block 53, in fluid communication with

^ O der Vantilkaiiiiner 54. An outlet manifold 54e di ~. Valve blocks 54 connect to functions 55, ci <? ixi inlet housings GO extend, which are provided at the other ends of the piston and cylinder arrangements 20 instead of the valve blocks 35, which are used in the embodiment of FIGS. Each of the inlet housings 60 merely forms a direct fluid connection with the fluid chamber 23 of the respective cylinder 21.

The device of FIG. 4 otherwise corresponds to that which has been described in connection with the embodiment of FIGS. The chilled,

expanded gas could come out of the radial openings 21c 35

are then released when the piston 22 is their inner Reach the end position, and then through the circular "shaped Sammeilextung 27 and lines 28 to the inlet of the heat exchanger 40 are passed. That again-

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heated gas would pass through lines 46 into the bore 2a of the. Hollow shaft 2, from which it flows back to the inlet side of the compressor 30. The pressure fluid outlet of the compressor 30 is introduced into the valve chamber and thus together into the piston and cylinder elements 20.

However, Figure 4 illustrates, as an alternative solution, a further embodiment of this invention where a talc valve is used to control the discharge of the cooled, expanded gas from the respective pressure flow channels 23 during the longest time of the outward reverse stroke to control the piston 22. This arrangement has the advantage that the Ge-Xi "rite Gan is added under effective pressure as it flows to the heat exchanger 40, instead of on the Saugünterur'ick of the compressor 3 0 _r to be dependent as described in the case of the previously Application forum is.

A z'v'eitei radial flange 26b is provided at the opposite end of the hub 26 carrying the cranks and carries a cam plate 51 by means of suitable screws 52. The cam plate 51 ^; is provided with an axially projecting control projection 51a. A control valve block 70 is suitably attached to the outer surface of the side wall 12 of the rotating support 10. The valve block 70 is similar in function to the valve block 53 and defines a valve chamber 71. The chamber 71 includes a valve seat 71a with which a stem valve 71b cooperated under the bias of a spring 71c. The shaft 71d of the shaft valve 71b protrudes through suitable openings in the valve seat 70 and in the side wall 12 of the rotating support 10: so that it periodically comes into engagement with the control projection 51a when the hub 26 carrying the cranks with respect to the rotating working shaft 2 performs an oscillating movement.

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"t / l-

The inlet portions of the valve channel 71 are respectively through lines 128 with a fluid control head 60 connected, which is attached to the outer end of each of the cylinders 22 in place of the valve head 35 is that in the previous embodiments is used. As best shown in Fig. 6, takes the Ströisurg fluid control head 6 0 a pair of flow ™ iaittei ^ anaie 76 and 77, those with lines 56, which feed in compressed gas or are connected to the lines 128 for cooled gas, which lead to the valve connector 71 verlai; "'3n. The channel 77 can start from a sleeve 78 Be surrounded by insulating material that is mounted in the fluid control head 60. When the stem valve 71b is crier *, then cooled gas flows through the pipe 1 2S to the size of the heat exchanger 40.

In iTii operation, the exhaust valve 71b is normally during the filling of the pressurized fluid chambers 23 of the cylinders 21 with pressurized gas and during the inward direction Power stroke of the piston 22 is kept closed. When the pistons 2 2 with their outward Start the reverse cycle, then that arrives corresponding stem valve 71b engages the control projection 51a and is displaced into an open position. Thus, the outward reverse stroke of pistons 22 is used to effectively deliver the cooled, forcing expanded gas through the opening 72 into the inlet of the heat exchanger 40. From that point on the circulation of the refrigerant gas is the same as before

^ Previously described in connection with the other embodiments of this invention.

In all embodiments of the invention, the reaction force on the cylinders 21 carried by the expanding gas is generated, helps to maintain the rotational speed of the working shaft 2, and thus ka.m reduce the energy requirements of the system. However, those skilled in the art will recognize

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- Ca that any gas, including air, can be used as a cold flow medium, and that the phase transformation of such a gas to the liquid phase and back is not essential for the operability of the centrifugal piston expansion device.

When air is used as the refrigerant fluid in a device 1 embodying this invention, it is not necessary that air be closed ^; - "Eyklu" is provided. Thus, as best shown in FIG. 7, the cooled air discharged from the fluid pressure chambers 23 through ring manifolds 27 into the Raurrib area to be cooled can through soffits 7 and nozzle elements 8 With such an arrangement, an effective distribution of the cool air in the room can be achieved by arranging the working area 2 in a vertical position near the ceiling .4 of the room and the rest of the facility 1 , and Kwar the drive motor (not shown), the compressor 30 and the multitude of rotating piston and cylinder cylinders 20, arranged above the ceiling 4 of the room to be cooled 2 are recorded _r on deiti a conical guide surface 9 is attached.

Reference is now made to Figures 8 and 9; a Another embodiment of this invention is shown which is a centrifugal piston expander A1 for extracting heat and mechanical energy from a compressed gas. Such a facility is attached to a circular plate A10, which in turn is keyed onto a shaft A2, which by a suitable electrical or current medium-powered starter motor A3 is operated. A conventional fluid shaft coupling A4 causes the supply of pressure fluid to the inlet

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Richtuny, from an orbs-proof feeding tube through a hollow bored section A2a of shaft A2 and into a manifold A6. The expanded and chilled Exhaust gases are removed from the device by a conventional fluid shaft coupling A5 'and fed into a stationary drain pipe A5a. The Äi: -Ia coupling A5 stands hollow with another Section A2b of shaft A2 in connection, which, however, is secured by a suitable lock (not shown) insulated from aera hollow bored section A2a isr that receives the pressurized inlet gases. The vvellerbohrungsabschnitt A2b is with an outlet Ga3sammler A5b in connection.

Several 2-cylinder changing elements A20 are rigidly attached to one rotating support plate A10 attached. Any such Zylirii3 :: elti? -Iant forms a fluid pressure kairuner A20a. which has a longitudinal axis that extends from a point near the axis of rotation of the beam A10 extends to a point radially from the axis of rotation. Each longitudinal axis of the cylinder is A20 however, not arranged radially with respect to the axis of rotation of the shaft A2, but points to this one Evening up.

In order to optimize the performance of the device A1, there are so many cylinders A20 on the rotating carrier shaft A10 attached, just like somehow housed there can be. The exact number used will depend on a number of design factors such as about the pressure of the gas that is available to drive the unit, the space that is used to accommodate the Unit is available, the desired speed of rotation and the weight limits for this

^ ° unit. It can be seen that the larger the diameter of the individual cylinder is Λ20, the smaller the total number of such cylinders that are part of the Carrier plate A10 can be attached. In a similar way

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U »· 9« ■ • ■ <

> · Ac

Way increases the length of the cylinder A20 significantly · the centrifugal forces acting on such cylinders, and thus makes an increase in the weight and strength of the cylinder component Ä20 necessary, as well as the carrier mounting plate A10 and the power-driven shaft A2. In the particular, illustrated in the drawings embodiment six such Sylindereinheiten A20 are shown, and they are each ^"\:. Ei.ls en carrier plate is secured by bolted A10 A21 bands.

A free piston A25 is mounted in each of the bores A20a formed by the cylinders A20 for sealed sliding movement along these bores. Since the hole A20a having a -Cylindrical training, conventional piston rings (not shown) may be used to the piston A25, it] provided but zönnsn the piston with a coating of an organic material äußeran ■ ■ ·, -.- rdexi that having good lubricating and Dichtungseigen- Schai-ciii, such as polytetrafluoroethylene, which ur.tssi "the DuPont trademark" Teflon "is sold, or a perfluoroelastomer piss DuPont under the merchandise." Kalrez "is sold.

The radial inward movement of each piston A25 is limited by a snap ring A20b, which is in the respective cylinder A20 is attached, and the outward movement by a shoulder A20c. At the outer end

^ Q of each cylinder A20 is a auswärtsvorspringender flange A20d provided to allow a valve unit A35 is secured thereto by suitable screws A35a. Each valve unit A3 5 (Fig. 10) comprises an annular block A3 6,

one central hole A36a and one enlarged one Limits valve chamber A36b, which is in communication with such a bore. A valve seat A37 is at the junction of the center hole A36a

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2> p

- 65-

and the enlarged chamber A36b, and a Shaft valve Λ38 works together with valve seat A3 7 and is normally urged to a closed, sealing position by a strong spring A38d. The spring A38d holds the valve A38 in its

gerchlc £ -eri_iri position, even during company dir.j '.-! Tic-i- :; with maximum fluid pressure in the

A20a.

The valve A38 is provided with a stem A38a ... which is located in the interior of the fluid pressure chamber A20a of the respective cylinder A20 extends, ur / d 3-flush with the outer surface A25a of a piston A25 engaged when this piston is its outer

¹ ^ has reached the end position in which it strikes against the inner shoulder A20c, which is formed within the cylinder A2G. In such an outer end position, the valve head A38b becomes the stem valve

A35 is raised in engagement with the valve seat A37. 20th

Pressurized gas is supplied to the valve chamber A36b through a conduit A6a supplied, which is connected to the gas distributor A6 which is concentric on the opposite face

the honing plate A10 is attached. As before-25

Mentioned ago, the pressurized gas in the manifold A6 is through the fluid coupling A4 and the hollow-bored one Section A2a of the rotating output shaft A2 is supplied.

From the description made so far it can be seen that that the pistons A25 in their outer positions in the respective pressure fluid chambers A20a move the centrifugal force generated by the rotation of the working shaft A2 from the starter motor A3.

When each piston A25 moves to its extreme position approaches, it comes into contact with the inwardly projecting valve stem A38a and moves the valve A38 into its open position, against the

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-26-

Preload of spring A38d. Sorait becomes a filling from pressurized gas into the outer end of the cylinder socket A20a initiated the outward movement of the piston to stop, and it will be when the pressure of such. Fill is high enough, each piston A25 inward moved by the force generated by such a gas. It can be seen that, when each piston A25 moves inward, the centrifugal force, which acts on the piston decreases, so that once the inward movement has started is set, it continues.

As already mentioned before, the reaction force of the filling of pressurized gas is exerted on the end wall of the Druckströmit.ur.gsEii ctelkammer A2öa. This force is shown in the control panel in FIG. 9 by the arrow labeled F_. It can be seen that:. · Effective torque exerted by the force F, the product of such a force and. ΰ-air. Distance R is the 'between the axis of the "Druckst.röütungs: nittelkainmer A20a and the axis of rotation of the hollow beam A10 and the shaft A2.

When the piston A25 with its inward movement ^ ^'J _f prone t he allows the shaft valve A38 to close and therefore the filling of the compressed gas include. Expanding this gas, and then cooled ,, while it acts on the piston A25, him to push inward. the expanded, cooled ° ^υ gas is discharged through a second valve member having a number of radial openings A20e that are formed in the cylinder wall and the piston A25 immediately before it reaches the end of its inwardly directed stroke, An annular collecting line A27 is arranged around the outlet openings A20e and leads the expanded and thus cooled gas filling through a line A27a and thus to the exhaust manifold A5b and

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to the stationary exhaust pipe A5a through the fluid coupling A5.

If it is desired to optimize the power generating properties of the above-mentioned device, then it can be seen that the more pressurized gas that is introduced into each pressurized fluid chamber A20a , the greater the reaction force and rotation that will be generate a torque that is exerted on the rotatable carrier A10 and dia Well.s ~ 2. In accordance with this invention, a conventional adjustable dampening cup A39 (Fig. 10) is provided, of choice. To control the extent to which the stem valve A38 is returned to its fully sealing position and thus to extend the period of time during which a pressurized gas is permitted to enter the pressurized flow medium through A20a. The damping container A39 comprises an oil-filled chamber A39a formed in the block A36, in which a piston A39b slidably operates. The piston A39b, in turn, is attached to an "outwardly projecting stem A38c provided on the outer surface of the stem valve A38 Flow of fluid through piston A39b during outward movement of stem valve A38, but provides an obstructed passage for any fluid flow when stem valve A38 attempts to return to its inboard sealing position. Thus, the length of time that pressurized fluid chamber A20a with a source of pressurized gas can be conveniently changed by changing the setting of the adjustable check valve A39c.

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Reference is now made to FIG. 11 in which like numerals represent corresponding arrangements; dorc is the centrifugal piston expansion device A1 shows the function as a room air cooling device is connected, wherein a refrigerant fluid is in a closed cycle in around? .on is located. The quay fluid can be any the known refrigerant gases, such as Fr-üon, but can also be an ordinary gas or air form, as the cooling cycle used is not the Requires conversion of the gas to a liquid and vice versa as part of the refrigeration cycle.

A heat exchanger A40 is rotatably mounted about the working shaft A2 '. Lines A28 are provided. - The heat exchanger A40 has a first EaOn ^: .attteil A41, which receives the ends of the Strörau.rigs ^ ii: tc-l lines A28. In the immediate compartment to the end plates A41 a collecting line A42 is provided, which a holder for several, with a catch distance arranged, axially extending tubes ΙΛΖ , which are mounted with their opposite ends in a manifold A44, which is formed similar to the manifold A42. A ζ front end plate A45 is attached to the second manifold A44. Annular chambers A41a and A45a are respectively attached between the end plate A41 and the manifold A42 or between the end plate A45 and the manifold A44 A45a is ηit the bore A2'a of the hollow shaft A2 'connected by radial openings A46, which thus it the

Allow 3 ^ reheated gas to pass through the hole A2'a the hollow shaft A2 'to the inlet of the rotating compressor unit A30 to flow on the other side the circular mounting plate A10 in that position

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installed beforehand by the Druekga ever boiler Λ6 was taken. The stationary sections A32 of the; Compressor A30 are attached to a bracket A32a, the outlet of the rotary compressor Ä30 is connected liDer Laitungen A34 with the Einlv Böff nurigen in the side walls of the valve units A35 are provided.

To use the device described in a device £ - ' ^v * ^T * l; r - "=. Ii, i or air conditioning, all that is required is a suitable controller and a fan to move a stream of warm air laterally over the rotating heat exchangers / upper A43. Such a harmonious piping is not shown, but rather complex ; the air to be cooled is shown schematically 11 denoted by arrows.

The operation of the device described above will ohn-v- further apparent to the person skilled in the art broom.; !. level facility becomes a closed circuit stream formed from a suitable refrigerant fluid. It is connected to the output connections A33 of the A3Q compressor started; such a stream extends through lines A34 up to the valve heads A35, which are attached to the outer ends of the cylinder elements A20 are provided. When each stem valve A38 is in its open position through the correspond the free piston A25 is raised when this i. arrived in its outermost, radially outward position then a filling will be made. Pressurized gas fed into the pressurized fluid chamber A20a, which is formed within each cylinder A20. Such a filling of compressed gas causes the axial Movement of the free piston A2 5 to a radially inner position with respect to the axis of rotation of the working shaft A21, against the counteraction of centrifugal force, iie from the rotation of the pistons

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this axis is applied.

When each free piston Λ25 has reached its most radially inward position, {3 v / how it is determined by the stop ring A20b, then the outlet ports A20e are opened, and the expanded, cooled gas is thus passed through the ki ois ring-shaped manifold Λ27 and the lines A28 routed to the inlet side of the heat exchanger A40. The suction exerted by the compressor A30 supports this gas movement * The expanded, cooled Gas passes through the heat transfer pipes A43 of the Vvärir.eciustauschers A40, whereby there is heat from the Absorbs room air that passes over this pipe, and is heated in the process. The reheated gas is through the outlet openings A46 in the'Bohrung A2'a of hollow output shaft A2 'and then into the fluid inlet of the compressor A30. .

The main advantage of the facility described above consists in the fact that during the expansion movement of each piston A25 as a result of the pressurized gas filling the React: .ons force of the expanding gas on the outside The end of the fluid pressure chamber A20a is exerted, and that this force is in one direction takes place to contribute to the rotation of the output shaft A2. Thus, the energy needs to operate this system as a result of the withdrawal of mechanical energy from the expansion force of the compressed gas be reduced. More importantly, the number of moving parts has been significantly reduced.

The skilled artisan will appreciate that the device described above results in ³ ^ turverringerungdes refrigerant gas only a certain range of temperature, which is determined primarily by the extent to which the gas is expanded. If the purpose of the facility is to effect room cooling, and the area of the

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Temperature decrease in the order of 16.7 K, then it is apparent that the temperature of the pressurized gas, entering into the plurality of piston and ZyIindereiementen A20, may not exceed 38 ⁰ C or less betragen.kann to any effective hatred to result in room cooling.

It can also be seen that the effect of the compressor Λ.7 0 büira compressing the reheated gas inevitably increases the temperature of the gas. Accordingly In most cases it will be necessary to use the compressor A3 0 and the drive motor for the Äro-eitswelle A2 'in a separate room or to accommodate an IvrTr.rier that is trarcHed by that Chamber: that must be cooled by means of a suitable wall made of heat-insulating material. Since the piston and cylinder elements rotate, A20 can such a W & rid most convenient between the rotating Carrier A10 and the heat exchanger A40 arranged:

be.- as shown schematically by the reference sign A7 in Fig. 11 is designated.

E £ may also be required, the compacted gets, that leaves the compressor A30 to pass through a cooling device in the manner of a heat exchanger, and this device (not shown) should be placed on that side of the heat insulating barrier A7, facing away from heat exchanger A40. The fan (not shown) for any such gas

SQ cooling heat exchanger can easily be driven by the working shaft A2 '.

Reference is now made to Figure 12; there is shown a modification of this invention wherein the device ° A1 is constructed so that it operates as a room-air cooling apparatus, said air refrigerant fluid .n an open cycle is used ■. Thus, the expanded air that flows from the pressure sm: i -tel chambers A20ä through the circular

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annular manifold A27 is released into the

Hardly directed area that is to be cooled, and. through lines A8 and nozzle elements A8a, which in turn rotate. With such an arrangement, a very effective distribution of the cool air in the room area can be achieved by the working shaft A2 'ir; a vertical position near the ceiling C of the room and the remaining parts of the device 2 \ 1 _f namely the drive motor (not shown),

jQ the compressor A30 and the multitude of. Cylinder elements ä2C, each containing a free piston A25, above the ceiling C of the room to be cooled attaches. IU "- .: k guided air can comfortably from the open End of de: -: Arbeitsswelle A2 'are included, at which what a conical guide surface A9 is attached.

From the foregoing description it will be apparent since "this invention can be used to both mechanical energy as well as heat to a compressed gas withdraw in order to act as an air cooling system, which corresponds to a closed cycle according to the execution criteria of Fig. 11 as well as in an open cycle according to the embodiment of Pig. 12 works with air as the refrigerant fluid.

All the. ;;? Embodiments of the invention can be found in their operating properties are significantly improved as a result that one is the length of the pressurized fluid chambers A20a the cylinder A20 increases. As previously in connection with the embodiment of Referring to Figures 8 and 9, this is the reaction force torque applied to the rotating carrier is applied, the greater, the longer it is the compressed gas filling is allowed to work on the free piston;, ": en. On the other hand, if the refrigeration capability of the facility is the predominant factor to be achieved then increasing the length of the pressurized fluid chambers A20a allows a greater one

BAD ORIGINAL ORIGINAL INSPECTED

Degree of expansion of the enclosed filling from compressed gas, so that a greater degree of cooling effect is achieved. These goals can be conveniently set according to embodiment can be achieved, which are shown schematically in Figs.

Reference is first made to FIG. 13; an Arrie-ir: ve.lle A2 drives a circular carrier plate Al C a: -. Lf_ ε cylindrical elements Λ120 are attached to the ro ⁱ -ier-i .-- i-äsr _i support A1 0 by means of straps A21 and w «: rr1c: n through lines A106 in the same way as previously described with pressurized gas , and the cooled, expanded gas is removed from the cylinders A120 through an annular sanitary line Al 27 which surrounds a plurality of radial openings Al21. However, each of the cylinders A120 defines a pressurized flow means chamber A120a which r.war has a uniform cross-section twvE but a curved longitudinal axis, thereby increasing the effective length of such a chamber.

If the main purpose of the device is a drive motor, then the pressurized gas is supplied from a manifold similar to manifold A6 of Figs.

If the main purpose is air cooling, then the pressurized gas is released from the outlet of a rotating compressor similar to the rotating compressor A30 11 and 12 are supplied. The pressurized gas source is thus designated schematically with A13 0.

For use as a drive motor, the exhaust gas is fed through lines A128 to a collecting device or a muffler; for air cooling purposes, it is directed into the space to be cooled off in accordance with he ^ s fill tion form of the Fig. 12 or to a heat exchanger according to the embodiment of FIG. 11, as schematically illustrated RRIT A140.

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In the embodiment of the Pig. 14 are the cylinders Al 20 with longitudinally curved fluid ^ chambers A220a provided, but the amount of curvature such chambers is chosen such that the end wall A220b of the fluid pressure chamber is generally radial arranged with respect to the axis of rotation of the working shaft A2 is. This means that the reaction force is that of the expa -. 'Iiförend3n Gas is exerted at the extreme end of the cylinder Α22Ό, at one furthest from the axis of rotation remote radial position is arranged, so that the reaction moinent, which is communicated to the rotating carrier A10: reaches a maximum.

In the embodiment of Fig. 15 is a single ° Zylinäerclert-ent used A3 20 having a Druckströinuii-gsiuitt.elkammer defined A32Oa, which has a spirally-2 formation and by more than 3 60 ° · about the rotation axis of the working shaft A2 extends. Thus an ai: 3 very long movement path for the free one

Plunger provided, but at the expense of limitation the PnKahl of the cylindrical elements passing through the carrier plate Piü be worn on one. However köMnari several carrier plates 10 and spiral cylinders elemeni.e A320 can be used axially in a row on the output shaft A2 if the output power additional cylinder is required.

In each of these embodiments in Figs. 13-15 it is apparent to the person skilled in the art that conventional,

cylindrical pistons are not used. Instead, the free piston may be that shown in FIG Form a ball A6 0 occupy. Such a piston preferably comprises a thin-walled, outer one

spherical shell A61 made of metal, made up of two embossed 35

There are half parts that are welded together, as indicated by AG 1a, the ball with a layer A62 is coated from an organic plastic,

BAD ORIGINAL ORIGINAL'INSPECTED

both lubricating and sealing properties has, such as the plastics mentioned above, which are sold under the trademarks "Teflon" and "Kalrcz" will. In addition, in order to increase the weight of the piston A60, the interior of the hollow sphere is preferred filled in with a heavy metal AC3, the Qucck: 5i .'- ^ £ -r, - a massive bent mass or small lead shot-.C.y wich may include. It can be seen cu; ".;: the mass of the free piston A60 is greater, the greater the force of the gas pressure will be, which is necessary to overcome the centrifugal forces, the £ ui act on the piston to cause it to.!., before. be in any radially outermost position 6sr · curved, previously described pressure flow T.f.ittclkaKimern move inward. In addition, the fluid pressure causes the ratio moderately thin-walled shell A61 acts, the indentation one;., such shell that seeks it, the ümfar-.g the Kvigel J ^ oQ in even closer sealing engagement with the walls of the special curved pressure flow; Ltt.slkäinir - '?. r 211 press in which it is used.

As shown in Fig. 18, a piston Λ7 0 can also be used generally ellipsoidal in shape can be used. The piston A70 also comprises a shell A71, which is formed from two embossed half-shell sections, which are closed by a weld seam A71a are combined into one unit. A cover A72 made of suitable organic plastic, because of

® ^{ö for} its lubricating and sealing properties is applied to the outside of the ellipsoidal shell A71. The inside of the shell is in turn filled with a selected heavy metal A73, such as liquid mercury, solid lead or lead shot.

Those skilled in the art recognized that the minor axis of the ellipsoidal 1 piston A70 essentially the same,

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but should not be greater than the diameter of the particular longitudinally curved pressurized fluid chamber in which the free piston is to be used. In addition, the major axis of the ellipsoid should be; well be short, to prevent _r that eat the Enäabschnitte of the ellipsoid on the walls of the chamber when the curved portions of the particular curved in the longitudinal direction of the pressure ströinuregsmittelkammer, crosses,

Referring now to Figure 16, ". There is one v.'cit - ;. re embodiment of this invention shown where a longitudinally curved pressure flow ~ iriit'-eikeatvuer follows a spiral-spiral path,

! 5 en -: «. · Is represented by a spiral-helical longitudinal section of a tube A420, which is attached to the rotating working shaft A2 ^! is attached, in which it is attached to Kehreren radially projecting strut elements .MOO, which are welded to the shaft A2 '. The pressurized fluid chamber A421 formed by the helical-helical tube A420 extends from an end portion A42Ga, which is arranged at a radial distance with respect to the axis of the working ropes A2 ', to one end

³ ^ A42Ob, which is arranged close to the axis of the working shaft A2 ', but has an axial distance from the end A420a. Thus, in this embodiment, the working shaft A2 and the radial struts A400 form the rotating carrier on which the

spiral-helical tube A420 is attached.

A spherical free piston A60 is inserted into the pressurized fluid chamber used, which is formed by the tube A420. A conventional inlet valve

A435 is the pressurized fluid chamber at the radially outermost end A420a provided, and: a conventional exhaust valve that has radial ports (not

BAD ORIGINAL ORIGINAL INSPECTED

shows), as well as a manifold A4 27 are included used to supply to Druckströrnunysmittel Pressure flow fluid carcimer or the removal of the cooled, - expanded gas from it on the same Way to control how this related to the earlier. Embodiments, is described.

The JV: -. V; _ ^ c: rin will recognize that the many execution «fornvc-i-clisri-r invention, which hitherto in detail ha ^ chrj..i ^. .: -. offer the utmost flexibility in the design of a simplified device for extracting heat and / or mechanical energy from «ii -'- in compressed gas. Depending on the desired properties of the device, the individual construction can result in a device which generates significant amounts of mechanical energy from a single pressurized gas. However, the device can also be designed so that it primarily causes a cooling of the compressed gas for use in an air cooling system in an open or closed cycle, but still gains a mechanical energy transition from the expansion of the compressed gas to rotate the To support labor wave. Thus, the provided motor A3 is primarily a starter motor and is necessary for the purpose of bringing the device to a sufficient speed to keep the free pistons in their radially outermost positions. After pressurized gas is supplied to the extreme ends of the pressurized fluid chamber, the reaction force of the gas acting on the extreme ends of such chambers creates a torque which tends to increase or maintain the speed of the rotating working shaft. Thus, a drive motor, an air

Air conditioning system or an air cooling system with high energy efficiency achieved.

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Referring now to Figures 19-21, a modified device B1 for extracting heat and mechanical energy from a pressurized gas by a force expansion device is shown which is generally similar to the device previously described. Such a device is attached to a circular plate or carrier B10 which in turn is keyed onto a shaft B2 which is rotated by a suitable electrical or fluid pressure operated Änls.SEari: iO'cor B3. A conventional StrÖ-inu! "- Cj sii'iitfcei shaft coupling B4 causes the supply of pressurized gas to the device from a stationary feed pipe E4ci through a hollow-bored section B2a of the shaft R2 xxnä into a distributor B6. The expanded and cooled exhaust gases are fed from the device 331 through a conventional fluid shaft coupling BS and fed into a stationary exhaust pipe B5a. The exhaust coupling B5 is connected to another

^ O hollow section B2b of shaft B2-in connection which however by a suitable lock (not shown) is insulated from the hollow bored section B2a, which receives the inlet pressurized gases. The shaft bore section B2b stands in with an exhaust manifold B5b Link.

Several cylinder elements B20 are rigidly attached to the rotating support plate BIO. Any such cylinder element defines a pressurized fluid channel B-20a which has a longitudinal axis extending from a point next to the axis of rotation of the carrier B10 extends to a point which is radially offset from the axis of rotation is. However, each longitudinal axis of the cylinder B20 is not radial with respect to the axis of rotation of the shaft B2 arranged, but has a distance to this.

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In order to optimize the performance of the device B1, as many cylinders 1320 are attached to the rotating carrier plate B10 as can be undocumented there. The exact number used depends on a view! vo ~ \ design factors, such as the pressure c "r_H gas, which is for driving the unit for Verfüg-iriy, the space available for receiving the unit for postponement, the desired speed, the gewünachten power output or cooling effect and the Unit Weight Restrictions. It can be seen that the larger the diameter of the individual cylinders B20, the smaller the total number of such cylinders that can be attached to the support plate 310 will be. In a similar way

¹ ^ the length of the cylinder B20 erhöht- substantially the centrifugal forces acting on such a cylinder, and he ~ thus force an increase in the weight and strength of the cylinder components B20 and B10 of the Trägör-Hontageplatte and the power-driven

^ Wall 32. In the special embodiment shown in the drawing, six such cylinders B20 are shown, and they are each attached to the carrier plate B10 by screwed straps B21,
,

A free piston B25 (Fig. 21) is mounted in each of the bores B2Ca, which from the cylinders B20 are formed, namely for displaceable and sealing movement along these bores. Because the hole

or pressurized fluid chamber B20a of the cylinder B20 is cylindrical in configuration, conventional Piston rings B25a can be used on piston B25, but the pistons could also be fitted with an outer Coating made of an organic material that has good lubricating and sealing properties has, such as polytetrafluoroethylene, which is sold under the DuPont Warem.eichen "Teflon", or a Perfluo: 'elastomer, which under the DuPont goods

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• -20-: v ν--:

sign "Kalrez" is sold. The pistons B25 are preferably formed from a ferromagnetic material. The radially inward one. Movement of each piston B25 is limited by a spring ring B20b mounted in the respective cylinder B20, and the outward movement is limited by a spring ring B2üc. At the outer end of each cylinder B20 there is provided an outwardly projecting flange B2Od, uη ¹ , to enable a cylinder head B26 to be installed by means of suitable screws. B26a is attached. Centrally an actuated by a solenoid inlet valve B33 is indicative avenge at each cylinder head B26 is _r which is connected by a line B6a with a Druckgasvexteiler B6 concentrically counter at the

-15 is attached to the surface of the mounting plate BIO. As mentioned earlier, is the pressurized gas' dex? Manifold B6 "fed through the fluid coupling- 'B4 and c.en hollow-drilled', section B2a of the rotating. Arbciifcsvelle B2 ¹ ... - '■ ■

The inlet valve B33 comprises a cylindrical, non-ferrous housing B33a, within which a ferromagnetic core or piston B3 3b is slidably mounted. The valve element B33c is screwed to the ferromagnetic piston element B33b and is normally by a spring . B33d pressed into a closed position a line B6a connects the interior of the valve housing, B33a with the Druckgasver- · divider B6 Finally, an actuating solenoid is about provided B33e around the central portion of the Veiitilgehäuses B33a such solenoid -.. · _r if it is energized, ^{causing the ferromagnetic piston 1} element B33b to be pulled down to operate the opening of the inlet valve element B33c.

works. '. "." - ^; "

BAD ORIGINAL OTIQINAL INSPECTED '; ^

tar «β ** **

From the previous description it can be seen that the pistons B25 in the respective pressure flow medium chambers B20a move into their outermost positions by the centrifugal force generated by the rotation of the working shaft B2 by the starter motor B3. >-ar; n the pistons B25 have reached their outermost positions .. ascA is activated by the operation of a control valve «c ;, the. In the following it will be described that the Ele-ki: rt, :: ia9net-operated inlet valve B3 3 is operated, ura

j, Q KU öff.r. (Sr. and to allow a pressurized gas filling introduced into aia pressure fluidizing agent chamber B20a will. If the pressure of such a gas filling is sufficient is high, then each piston wix'd stopped in its extension and inward against the Fli <sh> .matures.-preload moved by the Force generated by such a gas ". It is can be seen - that when each piston B25 moves inward moved-, the centrifugal force that acts on the piston, decreases, so that when the inward movement of the Kolbs ";; s is set in motion, so too for-rti-ühren v; ird The pistons B25 can through lead inserts 1: become a sword when an additional weight is required.

As discussed earlier, the reaction force will be:

of the pressurized gas charge is exerted on the end wall of the pressurized fluid chamber B20a, shown here as wall B26b of the cylinder head B26. This force is shown schematically in FIG. 2 by the arrow with the reference F _n . It can be seen that the effective torque / that is exerted _{by the force F n.}

is the product of such force and the perpendicular distance that is between the axis of the pressurized fluid chamber B20a and. the axis of rotation of the carrier B10 and the shaft B2 is present. -So is the moment arm for F is a constant.

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· ♦

After each piston B25 has begun its inward movement, the niagnet-solenoid operated inlet valve B33 is closed in a manner which will be described below, thus including the pressurized gas charge. This gas is then expanded and cooled while acting on the pistons B25 to drive it inward. The expanded, cooled gas is released through a second valve element, hereinafter called the outlet valve, which has several radial openings B20e which are formed in the cylinder wall and which are released by the piston B25 immediately before this piston reaches the end of its Einwai ^: ..shubes reached, ie at the end of the

Druclcströmiiianysmittelkaramer B20a has arrived. A kicJ .. · :, ^v : inc-shaped collecting line B27 is arranged around the outlet openings B20e and conducts the expancisrU: arid thus cooled gas filling through a line B20 r - ui'i Ah> gas collector B5b as? Ie to the stationary outlet On door ¹ - G B5a, the fluid coupling B5. . '_ ■ -., ■

Es Vv ^T ir ·. '? only; Referring to Figure 22; There is shown a discrete control circuit for operating a coil-controlled intake valve B33, denoted BV1, BV2 "... and BV6, respectively. A pair of measuring devices BS1 and BS2 are on each of the cylinders B20 provided in order to emit a signal whenever the free piston B25 is close to the position of such a measuring device The measuring device BS1 is preferably arranged so that it then supplies a signal when the free piston B25 is in its outermost or farthest position All of these signals are fed into a conventional electronic circuit B50 known as an "AND" circuit

and an amplified output for the application of power to all solenoid controlled inlet valves BV1, BV2 ... BV6 are only released if all free BAD ORIGINAL

ORIGINAL INSPECTED

Piston B25 have reached their furthest point. It is therefore ensured that all of these; Piston to been excited at the same time, so that thus a provision for the substantially synchronous inward movement the piston is given and thus the dynamic balancing of the rotating assembly is maintained is.

The last .MeßfüMsr.- BS2 are arranged on the cylinder B20 £ - a point radially inwardly opposite the MeßfüMsr.-, S1. The exact location of the sensors B 3 2 depends; depends on the amount of pressurized gas that one wishes to introduce into each pressure fluid chamber B20a, where the aim of the device is primarily to convert the pressurized gas into mechanical energy, Then the excitation circuit for the valves BV1, BV2 ... BV6 should have a self-retaining feature, and the sensors BS.2 are then each arranged far inside the sensor BSI in order to ensure that the pressurized gas is applied for as long as possible If, however, the aim of the device is to achieve maximum heat extraction from the pressurized gas, then the sensor BS2 is moved to a position which is much closer to the sensor B ₁ Si, so that the Inlet valves BV1, BV2 ... BV6 are closed by the action of the sensors BS2 shortly after the start of the inlet movement of the free pistons B25, so that the maximum expansion of the respective pressurized gas bearings is achieved conditions can. Sensor BS2 can be omitted and valves BV1, BV2 ... BV6 are closed by interrupting the signal from sensors BS1. The sensors BS2 are connected by a second "AND" circuit B51.

closed to actuate a relay B52 which controls the supply of actuation current to the solenoid controlled Inlet valves BV1, BV2 ... BV6 blocked. Each of the measuring sensors BS2 can also be connected to a separate

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Booster circuit and a relay connected directly to the corresponding valve BV1, BV2 ... BV6 so that each of the valves is closed as a function of the piston of the respective cylinder, instead of closing at that point in time. acts reach the layers in the Druckatrömungsmittelkammer in which all the free piston, the κ the mounting a share of the sensor BS2, respectively. Thus, the length of time in which the Druckströmimgsmittel chambers 320a connected to a pressure gas source, iu conveniently _r changed by that one changes the position of the H -.- UüberbIor BS2 with respect to the cylinders B20 or, more precisely, changes the position in which the respective free piston B25 causes the actuation of the sensor BS2 in order to close the respective Drackströmiriungsruitteleinlaßventiles BV1, BV2. To cause BV6.

In the control process shown in FIG on ei J. ie piston B25 together by a gas filling cincj: i-, irkt and they thus begin their respective Forward shub at the same time. In this way, the Pistons, kept reasonably in sync, and the dynamic alignment of the rotating components is there ensured. It may be preferred to use the piston to actuate two diametrically opposed cylinders at the same time and together and then periodically following the remaining pairs of diametrically opposed pistons on top of each other-

To actuate ^ O and applying the following force thus intermittent pulses if this is the main purpose of the device, or periodic pulses cooled, expanded waste gas for cooling purposes, if this is the main purpose of the device. This control process is illustrated schematically in Figure 23 in which each of the sensors BS1 is now labeled according to the particular cylinder to which it is applied. Thus the sensor is

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1 drawing BS1-1 on a selected one of the cylinders B20 used, and a sensor with the designation BS1-4 is applied to that of the cylinder B20, which is the first

'mentioned cylinder is diametrically opposite. The measuring

5 sensor designation BS1-2 will be similar for a "second Cylinder that is adjacent to the cylinder.,

s whose HeSsensor bears the designation BS1-1, and the

Msiifüh. "Erbozeichnung BS1-5 is applied to that cylinder - ariuz. Ae.r this cylinder is diametrically opposite.

The ν; - :, · "-]?.: Bond two cylinders bear the sensor mountings BS1-3 and BS1-6. Each of the pairs of dlaiaerrally opposing cylinders are connected to their respective sensors by separate "AND ^ Schaltur.gei-D ..- 5a _y B55b and B55c, so that no signal is generated by any special" AND "circuit, bit not the Pistons in the respective pairs of two opposing cylinders have both reached their outermost outer position. The outputs of the "AND" circuits B55a, B55b and B55c are connected to fixed, arcuate segments of a mechanical WevK'-escrommunikeinrichtung or switching device or timing device B6 0 Switch B6 works together with a rotating, diametrically running contact rod B61 on the working shaft B2, ² ^ which causes the respective connections of the "AND" circuit B55a, B55b and B55c with solenoid operated inlet valves BV1 and BV4, BV2 and BV5 as well as BV3 and BV6, but the actuation of each pair of valves is delayed by a period of time ^{equal to} one rotation d0 of the working shaft B2 by 120 °. Thus, the diametrically opposite piston pairs B25 are actuated together, but in a chronologically staggered sequence.

If a very short opening time of the inlet valves BV1, BV2 ... BV6 is desired, this can be done by d <? N mechanical switch B60. If a longer opening period is desired, then the

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33 333

Control circuits for the solenoid coils B33e dear valves BVl, BV2 ... BV6 comprise a conventional holding circuit (not shown) which controls the valves BV1, BV2 BVG holds open until the relay. B57a, B57b and B57c can be opened by actuating the sensor BS2.

Referring now to Figure 24, xvelcher the same reference numerals, corresponding ones already described above Denote arrangements; there is an

IQ richtPiig BI shown connected in such a way that it is effective as Ruu.u: air cooling device, whereby eiii cold fluid in a closed cycle in ΠιλΙ? ·. ■.: £ is brought. The cold fluid can irgenih ir <- s of the known refrigerant gases, but can also irvjor.a form an ordinary gas, such as nitrogen od ^ r air, since the cooling cycle used is not clic Uiiivrano.lung of the gas into a liquid and vice versa This is part of the refrigeration cycle.

rri.n heat exchanger B4 0 is installed around the work / eile ü2 '. B28 lines are provided, which each Jcreisringf örmige bus B27 that receives the geleühlUG ₇ expanded gas charge connected to the inlet heat exchanger dss B4Q. The heat exchanger B40 comprises a first end plate part B41 which accommodates the ends of the fluid lines B28;. · "-. In the immediate vicinity of the end plate B41 a manifold B42 is attached, which provides attachment for a plurality of circumferentially spaced, axially extending tubes B43 which are attached at their opposite ends to a second manifold B44, which is generally similar to the manifold B42. A second end plate B45 is attached to the second manifold B44. Annular chambers B41a and B45a are between the end plate B41 and the manifold B4 2, respectively formed, as well as between the end plate B45 and the collecting line B44. The chamber B45a is with

BADORiGlNAL

connected to the bore B2'ci of a hollow shaft B2 ', through radial openings B4G, which thus enable the reheated gas to flow through the bore B2'a of the hollow shaft B2 to the inlet of a rotating compression unit B3 0, which is located on the other side c.;: - the circular mounting plate B10 is in the position ώnc.ebrächt previously from the compressed gas distributor einjenor.r.icr; became. The spatially fixed sectons B32 of Verciichr ^ rs B30 are mounted on a support B32a Dc · · Aa ^ .La2 c.es rotary compressor B3 0 is connected by means Lsitun ^ s- Bjoa with the inlet openings in c-'ij;;: ·.:.? T '/ Av / changes of the magnet coil actuatedi EinlciJ- / Kr.-ilei'; h: -: it B33

To use the device described as an air cooling or air conditioning device, it is necessary to provide a suitable conduit and a fan to move a stream of warm air laterally across the rotating heat transfer tubes B43. Such a conventional guide guide is not shown; instead, the air flow to be cooled has been indicated schematically by arrows and explanations in FIG. 24.

The operation of the above-mentioned device is the Expert ohr.e further evident. One stream one suitable cold fluid is circulated through the described device in a closed loop educated. If you use the output arias B30b

^ O of compressor B30 begins, then extends a such flow through lines B30a to the solenoid operated Intake valves B33 provided on the outer ends of the cylinder members B20. if the control circuit of Fig. 22 is used, then all of these valves B33 are open when all free piston B25 have reached their extreme position. When the operation according to the control circuit of Fig. carried out wire, then the valves B33 one

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33

each pair of diametrically opposite cylinders is then opened when the corresponding pistons B25 of the pair of cylinder elements have reached their outermost position. In any case, does the An v? At the end of the gas pressure from the compressor B3 0, the respective piston B25 moves inwards against the counterforce from the centrifugal force. Once a motion has been covered more than one selected distance d raw 0 BS2 besT-irr-it of, mounting location of the sensor elements. is, the respective intake valves B3 3 are einschlössen and the gas filling is enclosed, and thus expands and cools, while continuing _t the respective pistons B25 inwardly to press. The torque generated by the expanding gas is applied to the outer end of each cylinder E2ö and provides a torque to assist the rotation of the entire rotating assembly.

V, KWVx öer free piston B25 at its radially innermost position: r-koTsmer. which is büstinunt through the stopper B20b, then the outlet openings B20e are opened. "i .: _; -: r. and the expanded, cooled gas is thus through the annular collecting line B27 and through lines 328 to the inlet side of the heat exchanger B40. The suction exerted by the compressor B30 supports this gas movement. The expanded, cooled gas passes the heat transfer pipes B4 3 of the heat exchanger B4 0, where it absorbs heat from the room air, which passes over it, and is heated in the process. The re-heated gas is passed through the outlet port B46 into the bore B2'a of the hollow working shaft B2 ¹ and then into the fluid inlet of the compressor B30.

As mentioned above, there is the particular advantage of the foregoing described plant in that during the Expansion movement of each free piston B25 by the pressurized gas filling the reaction force of the

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expanding Gcises acts on the outside end of the pressurized fluid chamber B20a, and that this There is a force in such a direction that it assists the rotation of the working shaft B2 '. Consequently

'f 5 skills: the energy requirements to operate them

\ Plant, as a result of the withdrawal of mechanical energy

r from d :: r expansion of the compressed gas can be reduced.

Even more v; ^; - more real is that the number of movable parts. 1 e

bstrrclcr.tij.oh has been reduced.

10

The? A.] \: Ua; -n will recognize that the device described above brings about only a certain range of temperature reduction of the refrigerant gas, which at first.-; Line is determined by the amount by which the GiiO Gxr-snäiert. If it is the purpose of the device xsZf to effect the room cooling, and the range of temperature decrease in the order of 16.7 K, then ersiehtlichorweiso the temperature of the pressurized gas, entering into the plurality of Eylinderelemente B20 must, 38 ⁰ C odex ~ less do not exert themselves to provide any effective measure of restraint. It can also be seen that the action of the compressor B30 in compressing the re-heated gas will inevitably increase the gas temperature. Accordingly, in most cases it will be necessary to mount the compressor B30 and the drive motor (not shown) for the working shaft B2 'in a separate room or chamber which is separated from the chamber to be cooled by a suitable wall made of heat-insulating material. Since the cylinder elements B20 rotate, such a wall can most conveniently be arranged between the rotating carrier B10 and the heat exchanger B40, as is schematically indicated by the reference character B7 in FIG.

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· ": ■,": YYYYYZb

It may also be necessary to send the compressed gas leaving the compressor B30 through a cooling device similar to a heat exchanger, and this device (not shown) should be on that side the './ärmeisolisolierende barrier layers B7 arranged-. Gciri, which unwound from the heat exchanger B40. is. The fan (not shown) for any such gas cooling heat exchanger can be from the work in the meantime B2 'be driven.

ίο ■■■ -'-

Reference is now made to Figure 25; there is shown another embodiment of this invention, the Eir. rj.Cii.: ang B1 is constructed in such a way that it is effective as a Rau πι-Luft-iaihlvcrrichtung, where air is used as Käl.teströmur.:; öir.i-ttel in an open cycle. Sorair. vvirci the cooled, expanded air / · that from the .. DiTickstrramittelkamniern. B20a is discharged through the circular urinal collecting lines B27, into the area to be cooled through lines B8 and B8a ??;.:. the ends of such lines delivered _r which alli-rcirgs rotate. _# With such an arrangement a very effective distribution of the cool air can be achieved in the spatial domain, that one of the JRaurne5 the working shaft B2 ¹ attaches in a vertical position close to the ceiling C and the rest of the apparatus B1, namely eon drive motor (not shown) , the compressor B3 0 and the number of cylinder elements B20, each having a free piston B25, above the ceiling C of the room to be cooled. The recirculated air can conveniently be collected by the open end of the working shaft B2 ', on which a conical guide surface B9 is attached.

From the foregoing description it will be apparent that this invention is used in an apparatus which is primarily intended to extract mechanical energy from the compressed gas, such as represented by the embodiment of Figures 19 and 2Q

'BAD ORIGINAL

ORIGINALINSPEGTED

is. The principles of this invention can also be used to generate both mechanical energy air also extract Ivänria from a pressurized gas to use as an air cooling system in a closed cycle according to the embodiment of FIG. 24 and in an open cycle Cycle 7.i'.t air as a refrigerant fluid in coincidence -;: .-. ;;:. J to function with the embodiment of FIG -

All these embodiments of the invention can be significantly improved in their operating characteristics by lengthening the length of the pressure flows through the cylinder B20. As mentioned above In connection with the embodiment of I ¹ Lg = 19 and 20 mentioned, the longer the filling of the Drv-jkgases can act on the free piston, the greater the torque resulting from the reaction force that is applied to the rotating carrier If, on the other hand, the cooling capacity of the device is a predominant factor to be achieved, then an increase in the length of the pressurized flow means in a B20a will allow a greater degree of expansion of the enclosed pressurized gas charge and thus a greater degree of cooling to be achieved Embodiment can be achieved, which is shown schematically in Fig. 26, as well as in other cylinder Ausbildüngen that so far bere its have been described.

° Q Reference is made to Figure 26 now, in which identical numbers represent components that have already been previously described. an inlet shaft B2 'drives a circular support plate B10. Cylinder elements B120 are attached to the rotating support B10 by means of belts B21 and are fed with compressed gas through lines B6ci in the same way as previously described, and the cooled, expanded gas is passed through the cylinders B120

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a circular collecting line B27 withdrawn.

which surrounds a multitude of radial openings B20e. However, each of the cylinders B120 forms a pressure flow means chamber BI 20a which, although it has a uniform cross section, has a curved longitudinal axis, as a result of which the effective length of such a chamber is increased. It is even more important that the extent of the K / .ürttaung of such chambers is chosen such that di-ß dia 'Δ \ linderendwand B26b of each chamber is generally arranged radially with respect to the axis of rotation of the working shaft B2'. This means that the reaction force exerted by the expanding gas in the extreme end of the Zy-IiIVr ₁ -Sr B120, with respect to the Drehaciu ^! e assumes the greatest possible radial position, and d ^: .T. ^f> . such a torque arm remains constant, so that L c.urf Ueaktionsdrehmoment, which is applied to the rotating carrier Bi C-rr.iL.3o ':. 3ilt, reaches a maximum value.

In the case of dsr Α:; οί guiding form of Fig. 26, the subject κι recognizes: · .ηη ,. that no ordinary, cylindrically shaped. Ko3.beη can be used. As before beach r live, - karui a spherical. Pistons used wer el sp, which has a surface coating made of an organic plastic that has both lubricating and sealing properties, such as. such as the above-mentioned plastics sold under the trademarks "Teflon" and "Kalrez". An ipsoid-shaped piston coated with such an organic plastic can also be used. Reference is made in particular to FIGS. 31 and 32; there is shown an ellipsoidal piston B70 which has two ferromagnetic half-shell sections B70a and B70b which are attached to one another by a circumferential weld seam B71. Vicinity

^ A range of diameters with the largest cross-section of the ellipsoidal piston B60 is a pair of piston ring grooves B72 provided, which each receive conventional piston rings B73. Such a piston can

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ORIGINAL INSPECTED

can be seen to traverse the curved sections of the central cameras, which are longitudinally curved: axes on iron. The inside of the piston B70 may be weighted with lead.

Reference is now made to Fig. 32; there is shown another roller arrangement. The piston B80 comprises an arrangement of two or more massive, natural ball elements 1381 and B82, which are pivotably combined with one another in ball joint B83. With this arrangement, each of the balls BSI and B32 can have an annular groove B81a and B82a for receiving a piston ring B84.

In ^ on ^ zn cases it may be desirable to locate the erwung. Exhaust of the cooled, expanded gases from: clor; To effect syiinderelemente, instead of au! any pressure difference between such G ::. sea ar.d to leave the ambient pressure, or tmf the gauging pressure of the 3 compressor in the case of an air conditioning system with a closed cycle. It can be seen that the outlet openings B20e in each of the f, yLinder B20 are only open for a very short time - while the free piston B25 is in its position closest to the axis. In order to overcome this problem, the embodiments of Figs. 27-29 were developed.

Referring first to Fig. 27; the ejection cooled, expanded gases from the pressurized fluid chamber B20a is actuated by a solenoid Effects exhaust valve B35, which is attached to the cylinder head B26. The exhaust valve B35 has the same structure as the solenoid operated intake valve B33 and thus includes a cylindrical, non-ferrous housing B35a, inside which ain ferromagnetic piston B35b is movably attached. A valve element B35c

is screwed to the ferromagnetic piston element B35b and normally biased to the closed position by means of a spring B35d. Lines B35 each establish a connection with the interior of the valve housing B3 5a through radial openings, the below the ferromagnetic piston element B35b are arranged. An actuating solenoid B3 5e is provided around the central portion of the valve housing ·; B3üTä provided. Such a solenoid is when excited, the ferromagnetic piston eleluanu Cause B35b to be pulled down, UiTS clas öfxneri of the outlet valve B35 to cause.

It will only. Referring to Fig. 28; There is shown a closed cycle system including the exhaust valve assembly of FIG. Ξξ wj rc notes that the lines B36, which lead away from the hu si a Sven ~ ii caught B3 5, are each connected to the Sanroelleitung 341 of the heat exchanger B4 0, ". The other elements of this arrangement are correct nait j <■ ;. : ·. Those previously described in connection with the embodiment of FIG. 24.

23 shows the application of the exhaust valve mechanism 27 in an air cooling device with an open Cycle that was previously described in connection with FIG. Exhaust pipes B26 represent a Connection of exhaust valves B3 5 with discharge nozzles B8a here. All other components are the same as in the embodiment of FIG.

. The Steiierschaltung shown in Fig 30, however, must be modified to produce a provision for the operation of the solenoid controlled exhaust valves B3 5 to proper points in time represented by the position of the free piston B25 in ^- is determined by the respective pressure fluid chamber B20a. Such an operation can through the

'BAD ORIGINAL ORIGINAL INSPECTED

-9ε-

Addition of a third sensor BS3 to each of the cylinders B20 at a point in the vicinity of the end of the pressure fluid chamber B2 0a near the axis. Thus, the sensor BS3 determines when the respective free piston B25 is its outermost inner or axially near '·. a position has reached. If every free KoI-ber. 3rd: ': ^ .r. If such a position has been reached, then the signal generated by the sensor BS3 is activated by a conventional logic circuit B65, and the respective exhaust valve B35 is opened. A conventional hold circuit inier.t inclined :) holds the exhaust valve B3 5 open. The Kessf'lcler BSI. . which are located near the outermost off-axis or lag · cles free piston B25, function duxoh an "AND" circuit B50 in the same manner, vis has been described in connection with Figure 22, -... i * m the correct opening all solenoid spuleng esteut'.tsu inlet valves B33 to be effected. The sensor BS2 now performs a double function. When the free piston B25 is activated, the respective sensor BS2 generates a signal which is effective through the logic circuit B65 in order to cause the respective inlet valve B33 to close. As the free piston B25 moves backward, the sensor BS2 generates a signal which causes the logic circuit B65 to generate a signal to open the relay B66 and cause the solenoid operated exhaust valve B3 5 to close.

^ So far it can be seen that the expanded, cooled Gas through the centrifugal-induced exhaust stroke of the free piston B25 through the solenoid operated B35 exhaust valves during a substantial portion of the outward stroke of these pistons is delivered. Thus, the cooled, expanded gas is forced to enter the inlet of the heat exchanger B40 in the embodiment of FIG. 29 or directly the room to be cooled in the embodiment of

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Fig, 3 0 supplied.

ge

-H-

Can as ührungsforrnen in the case of the embodiment described above, a control circuit similar to Fig. 23 (j can be used to control the opening of the solenoid-operated intake valves B33 to control such that pairs are fed from ζ v / ei diametrically opposed cylinders B20 gas zura same moment , but in a lateral assignment for feeding in compressed gas

] 0 to the remaining pairs of diametrically opposed cylinders. Thus, the arch-shaped. spriciifc = .. ruicfe or helical / spiral design of the pressure Lröniungsmittelkaitißiern, the previously described Vurcien _r together with the exhaust valves and the control circuit are used by the. Embodiments of Figs. 27-29 are shown. The Fachrtä.-m vi.rci recognize that many modifications in the previously bar-written invention require the utmost flexibility \ - ~:. \ Do.c construction of a simple device "for Providing energy from compressed gas. Depending on the desired characteristics of the device, the construction may result in a device which generates considerable amounts of mechanical energy from compressed gas, but the device can also be designed to do so primarily acts to cool the pressurized gas for use in an air cooling system in either an open or closed cycle, but in either case some mechanical energy input is withdrawn from the expansion of the pressurized gas to aid the rotation of the work B3, which is provided, primarily a starter motor, which is necessary for the purpose of bringing the device to a sufficient speed,

^ to keep the pistons in their radially outermost positions. After pressurized gas is applied to the outer ends of the pressurized fluid chambers, is generated the reaction force of the gas acting on the extreme

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H Λ. * · ■ A

• *

* A * it ♦ *

Ends of the chambers acts, a torque, dcis thereafter seeks to increase or maintain the speed of rotation of the rotating engine shaft. Consequently an air conditioning or air cooling system is formed with a main drive with high energy efficiency.

It vv-urae already mentioned that it is desirable to use elongated, rc "ii rending pressurized fluid tubes of possibly great length to either transfer the iin.vj'ha ^; .-,!. ^" · :: energy to increase, which is withdrawn from the compressed gas or the air that is fed in at the outer end of the Druckvcrömurnjsmittelkammer, or to increase the expansion and thus the cooling of the compressed gas, which is generated by the expansion of the gas in the elongated pressure strömungsraittelkaramer In all of the embodiments discussed so far, is the effective length of the pressurized fluid chamber. generally limited by the requirement that outlet openings must be established during the inward movement of the piston ¹ to the axis of rotation. It can be seen that when the piston has such outlet openings. passier tf ier nearest the axis of rotation of the elongate, rotating pressure fluid chamber is arranged, but it can not advertising permitted because of the centrifugal force the 'that it also passes over the axis of rotation, because that would then folding and the piston would radially move away from the axis of rotation, he left the outlet openings open. In addition, all of the aforementioned or in the above-mentioned application were openly based

^ ^U disclosed embodiments, either at a low ambient pressure, the expanded gases from the exhaust ports urn subtract, or on the inlet suction generated by a compressor, which was connected with the versions of the device with a closed cycle. In fact, the pistons were single-acting, that is, of mid-flow pressure

was only effective in one direction.

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WWW VW / V /

Anyway, it is desirable to provide rotating pressure flow means of greater length, which can be achieved by letting the pressure flow means can extend diametrically from one side of the axis of rotation to the other, provided that suitable valve arrangements are provided to facilitate the flow control a pressurized fluid at the end of the e'inen diametrically disposed elongated Druckströ-ii: ri-vr .'-; to allow mlttelkanuner when the Κο1) ΐ3η located close to this end, and the application einsK such Strörnungsmitteldiruekes substantially LATI se .. · ?: continue until the piston reaches the other end of the elongated pressure tube, which extends slightly from the egg, and van -; - sr .; itt el chamber reached. At the same time, the e'par.ciic rte, ejected fluid that originates from the vurar ;; existing stroke of the piston in the opposite direction; compulsorily from the other, .diametral to -U ¹ : .-? -! "! are displaced u-.er such an arrangement provides a maximum power output of the rotating T; eg en el he end of the elongated Druckströmungsinittelkar: CAEV - :. r what the diametrically extending, elongated · Drik kströmungsmittelkammer.!..? is appropriate.

On the other hand, when optimal air cooling is desired is, - then the valve assembly should be applying of pressurized fluid on the piston only for one; L'sitrauin. allow sufficient to ensure that it begins with the inward movement from its radially outermost position, after which the pressure ^ the fluid inlet is closed and the a-r closed gas filling during the entire stroke of the piston through the diametrically extending Pressure flow medium chamber is expanded.

A new charge of pressurized gas can be introduced into either end of the S-shaped cylinder which is located the piston approaches, and the exhaust valve is closed before the piston reaches this end

BAD ORIGINAL ORIGINAL INSPECTED

to cushion the end of the movement of the piston until it comes to a standstill and to prevent it from resting against the end of the piston. Closing the outlet valve can, however, also include sufficient gas in order to swallow the energy d -: * 3 piston, so that the opening of the 2ini :. i ',.-ntiles can be delayed until the piston iL .... · has come to a standstill. Thus a substantial part of the kinetic energy of the piston is transferred as a K-iaktionskraft to the neighboring cylinder * - enCviand in order to reduce the rotation of the cylinder i ät: -: er. _tr while the remaining energy is applied to the jerk. · art thrust of the free piston. It if-t can be seen / that if the speed of the ^! .vech: ~ älbew- = movement of the free piston a desired Hcchr-'t:;'..:;.:; achieved, either the pressure or the amount of ns -rhi owing pressurized gas filling s by conventional valve devices (not shown), is reduced.

All of the foregoing goals can be achieved through the establishment el be achieved, the schematise].! shown in Fig. 33: is. One such device includes a cylinder element C10 which is generally S-shaped Bore CIOe defines the pressurized fluid chamber for the establishment. The cylinder element C10 is preferred for rotation by means of a power-driven Shaft C2 attached. For this purpose, the cylinder element C10 can by means of several belts C12 attached to a circular plate C14, which in turn is suitably keyed or welded onto the shaft ° C2.

At each end of the cylinder element C10 are each other the same valve heads C20 are provided, each of which includes a solenoid-operated inlet valve C25, which control the supply of pressurized fluid from a feed line C25a. In addition, the includes Valve head C20 a solenoid operated exhaust valve C26, which is the outlet of the pressurized flow medium

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C10a allowed in an outlet line C26a.

A free piston C15 is arranged for reciprocating movement within the S-shaped pressurized fluid chamber C10a. Such a piston may comprise an ipsoidal piston, as shown, or it may grip a ball. In any case, the free piston C.15 is along the entire length of the S-shaped. Druckströmungsstmittelkc; -:; ..: ^ :: Cl Oa only movable under the influence of the Stror.uii-, -v.ridden pressure forces and the centrifugal force. He .i..oL can be seen that the centrifugal force in counter-. direction acts on the free piston C15 each time, vevui he passes the axis of rotation of the shaft C2.

To the Bv.-tr .leb of the pair of magnetic inlet valves C25 uEid of the pair of magnetic outlet valves C26 to s', eu ■ -. · - :; ι it is necessary that the position of the free Koi'r c-rv: 5 Ci in the S-shaped Druckströmungsmittelkammo-r CI Q'.i f C: L ^r t | ös is divided. Accordingly, a number of electronic measuring devices are at a distance of lr.nq ?. ; "..-- ;. the path of movement of the free piston C15. Thus, two devices C40a and C40b, which determine the presence of the piston, are provided in each case at the hub dc ^v ; Au genes of the S-shaped pressure fluid flow channel: or C10a, while two further, the presence of the piston fixed by bodies C4üc and C40d near the raittlereii Abschniten the Foex S ~ \; Xqt λ pressure fluid chamber ^r C10a are attached.
'·

While the measuring devices C40a to C40d can include either a conventional electrostatic or electromagnetic sensor, it is preferred an electromagnetic sensor and a free piston C15 with an ellipsoidal design are used, which includes a permanent magnet C16 (Fig. 34) generally on the major axis of the ellipsoidal shape Piston is aligned. The rest of the interior

BAD ORIGINAL ORIGINAL INSPECTED

- ^ of the free piston C15 can with Arcjondoimün κα1ιν? οτ (·> α Non-ferrous metal C17 filled up:; o.i.u, v; iR about Mercury or lead shot

The piston CI-5 preferably comprises a thin-walled cup CIS, rliv- aai - ': h the welding together of two punched Haib-b- ^ v: .t.te C18a and C18b is formed. The outer, ell Ip.:. 5 idf örnige surface of the piston CI 5 is with -eir; -. j ~. Bulgarian plastic material C19 coated. the cfiit v £ honor, which has and sealing properties, how etc.? with plastics covered by the Du Pont-V? a ret) - zeiebcu '-Tel: lon "and" Kalrez "are sold.

It π 1.TV. now referring to Fig. 35; there are scissors; "^ iscii p.in2 electronic circuit to control the solenoid valves C25 and C27 to effect the constant v.'rchse-lbev / egu.ng des Kolboneleraen fco CZ ^ ö roped over the length of the Sf örrai-jen Druckströmraungsmi ttelkamiT-sr C10a the measurement or Ermittlungseinrichtangen C4 0;. '.', ^'ΔΌ C4, and C4 ^ Ζϊ 0d are 0.O ο via a logic circuit C O ^ ncrer _chlossan-f to the required successive action of the solenoid-operated Einlaßventile-. C25 ur.u the solenoid actuation ton exhaust valves C26 ir. To deliver correspondence with the position of the free piston CI5 in the Druckströmungsiaittelkainmer CiOa.

Thus, when the free piston C15 is close to one of the diametrically opposite ends of the Druckström-30

MungstittelKammer CIOa is located, at which the Measuring unit C40a is arranged, then this measuring unit is activated by the logic circuit C50, to open the adjacent pressure inlet valve

C25 and a closure of the adjacent outlet valve 35

tiles C26. At the same time, the outlet valve C26 at the opposite end of the pressure flow means chamber. C10a open. The free piston C15 is correspondingly filled with compressed gas

BATH ORIGINAL

In each case, the compressed gas will, if no other control functions are provided, continue to be fed into the piston C30 in order to drive it over the axis of rotation, at which point the centrifugal force becomes effective to move it outward into the diametrically opposite one to press the extreme end position. During all the time during which the pressure fluid acts on the free piston Cl 5: a reaction force is exerted against the end face of the pressure flow device C1 Oa by such a 0 SLrCüriuncari'.ltfceldruck , so that thus c-iii Drehnioju. raU is applied to the cylinder element CtO and the tracer CI4 to help maintain or increase the speed of such elements.

ΐ * Γ · ΐΐ "ίΠ (3 free pistons C15 on the diametrically opposite side of the: Dneic the S-shaped pressure fluid chamber CIOa is attached, then its presence is determined by the i.nv.X longitudinal device C40b, and the soru.lf i -r '-'. ougte signal is sent to the logic circuit CSD eiKjaCj- ^ bsn, with the result that the pressure r.tro :: VJ.: - fj srui t Lei inlet valve C25 near the free piston is opened and the outlet valve C26 is closed

This allows the applied fluid pressure to padded the dov. Movement of piston C15 to such an opposite end, and a substantial portion of the energy resulting from such a padded standstill is expended in one direction that contributes to assisting the rotation of the cylinder C10 and thus the output shaft C2. In other words, part of the compressed gas energy is converted into a kinetic energy of the piston, which on the cylinder

3ö derkopf transferred at the end of each piston stroke will. Uni is the angular velocity of the cylinder CIO and wave C2 to increase.

ORIGINAL INSPECTIB BAD ORIGINAL

The outlet valve C26 on the diametrically opposite one The end of the S-shaped pressure flow jumper C1 Oa will open and the piston will reverse its movement through the S-shaped pressurized fluid chamber C 10a,

δ where ex acts as a double-acting free piston is. DJo measuring unit C40a is in turn excited by η, when acr free piston arrives in its starting position / wodu.rcr- the cycle is repeated.

If you want to optimize the expansion of the ü ;. ~ U ^r : kg-a.ses / which the ^{Druckströmip.uTi --- r} -iVi:. ~ Ti'lkavamer C10a is supplied, then you get ^ - ^ facilities C40c and C40d to effect. These Ξ in the direction of each generate signals when the frti-r piston CI5 passes them. Such measuring devices contour, be arranged near the axis of rotation, as shown; od & - with radial abs band opposite this.

The i: e '; devices C40c and C40d are both connected to the 1; ■;. ■! .- ■ Ji.-en circuit C50. "." The logic circuit C 0 is responsive to the excitation of the Aufnahmeeirjrichtung C4i) c characterized in that it includes the closest Druckstföjiiur.gsmitteleinlaßventil C25, V7elches Pressure -;! Fluid fed to the flask and / so-with the previously inducted gas behind the piston and allows such gas to expand during the remainder of the travel of the piston C3 0 to the diametrically opposite end of the S-shaped pressurized fluid chamber C10a. The measuring device C40d is responsive to the movement of the free piston C15 in the opposite direction to perform the same function. It can be seen that the permanent magnet C16, which is arranged in the ellipsoidal piston C15, generates an opposite S.ig ~ ηειΐ in the measuring devices C40c and C4 0d, depending on the direction of movement of the free piston 15 with respect to this, so that the respective backward strokes of the free piston 15 ciuf the control

jerky have no effect.

The Vorwendung the cooled, expanded gases generated by the above described means, b is effected on any of the ways previously described, ütiisijielsweisc can, as shown schematically in Figure 36 MC ^5: -: ': \ igi, the Äbgasleitungen C26a.. be connected to a Kiril / iu - \; :: n: oil line C61 of a rotating heat exchanger :: - j'-ö CCC. The cooled gas is through di .; axially extending tubes C63 are introduced into an outlet line C62, from which it is fed back via the line C6 6 to the inlet of a compressor C65, which for common rotation ii-.j ■ ;. the Arbertswolle C2, the cylinder element C10 and a * ? · .1ϊ1ϊ.- :; ^:: - '-. "C3 motor is driven, the pressure output of the compressor is C65 eince über.Leitungen C25a: -RK-ii.t, each having a connection with the r.ici ^ ri -.' :: - controlled intake valves. . Thus, to produce C25 egg; nit c h oh an efficiency Luftkliraatisioruiij'seinrichtung powered with a closed cycle on the G •• ■ ζ and j jvj cioè-r using the S-shaped Druckströmungr: - r ^ ^ itteik isür C based 10a .

There \: i -d Referring now to Figure 37 taken;. there is shown another embodiment of this invention wherein a rotating, S-shaped pressurized fluid chimney is used to supply cold air to the room in an open cycle facility. As schematically shown in Fig. 37, an S-shaped cylinder CIO, which is the same as that shown in Fig. 33, is attached to a vertically disposed working shaft C2 and is driven by a suitable motor (not shown). The cylinder C10 and a support plate (not shown) are both arranged above a ceiling C of a room to be cooled. Compressed air is supplied from a compressor C60 mounted at the top of shaft C2 through lines C25a to valve heads C20, which are at each end

BAD ORIGINAL ORIGINAL INSPECTED

• / IDS · of the S-shaped cylinder C10 provided. The cooled c expanded air is with lei :; Outlet duct C26a is fed through a suitable opening in the ceiling C to a pair of contour-shaped expansion devices C26b, through which the cooled air rotates in the. ru-ui-: «is delivered. The return of the room air can through the hollow bore of the working area C2 to the lic ';'_u in the inlet of the compressor C65 through a gee; ^r -Ci-n - t: - ^; . Line C66. Thus, the S-shape:. {Per pressure fluid chamber CiOa and the with it; -. Usanuuen-acting, ellipsoidal, free piston Ci5 can advantageously be used in a room cooling system with oiferu ^ .-: iy't-il'us.

Reference is now made to Figure 38; there is shown edne äbq ^ v ^ avidslte embodiment form of this invention, wcb? -: i <~: as S-shaped cylinder elements ClOO essentially · - " 7. - - C1 semicircular sections CIOOa ixnd CIOOb on ν: · _ ^ί.ι; tf which with their abutting Er.-d = n · .η de.r axis of rotation of VJoIIe C2 are mounted and .the V ^ _f r.tilköpfe C20 as previously described ,, at their diametrically opposed ends The cylinder element C100 thus forms an inclined pressure fluid chamber C101, in which the end walls of the pressure fluid chamber are both arranged in substantially radial planes with respect to the axis of rotation. This increases the torque to a maximum that is suitable for the Reaction force is available from the expanding gas

is exercised. Other elements of the facility are identical to those) / which have already been described previously in connection with the embodiment of FIG. 33 what were also the use of an ellipsoidal includes free piston C15, which has a permanent

magnet carries, as well as the use of four measuring devices C40a, C40b, C4 0c and C4 0d to each Pressurized fluid inlet valves (not shown) and the solenoid-fired exhaust valves (not shown)

ZLi stevedores.

Referring finally to Fig. 39; there is one? Another embodiment of this invention is shown, P ₁ wherein an S-shaped cylinder element C1 0, which corresponds to the embodiment of FIG. 33, is attached to a rotatable lath C14 and two additional S-shaped cylinder elements C210 and C310 each on eiric : ·: The sides of the element C10 are attached.

IQ The Z ;, Z i: "iit-.rcloniente C210 and C310 each embody S-form.v.ige I-1 ''. Back-flow-media-caraniern, ellipsoid-form for & ie Kcln-3n,. Which have a permanent magnet, scvis valve heads C20 each end of the cylinder elements Cs 10 ί, ί-c CL-20, which performed the same functions as the valve ^ cpfe C20 aas, which are provided at the ends of the central, S-shaped cylinder element C10. KoI-bivi'-iisS- 'Institutions C40a, C40b, C40c and C40d are efcc? " r.ills -'lit these two additional S-shaped Syliiiif'-ri-L'vUisnten provided, and these act with ώ '"^;" ι respective magnetic inlet and outlet valves in de: - VcnLiikönfen C20 together to the alternating movement the j'v.v, -.- ji.Il-jan free flask in the same way as her ·?: ·. ' . ·· · interrogation described to control. The outlet ducts C20a are a heat exchanger C60

2Ό connected, and a compressor C65 on the output shaft C2 supplies compressed gas to the lines C25a.

There can also be a plurality of single-cylinder units similar to the embodiment of FIG. 33 at the Working method can be attached axially one behind the other.

Those skilled in the art will recognize that the arrangements described above Training with the optimal length for längliö -> before, rotating pressure provide fluid chambers, within which a free piston merely passes through the Effect of pressure forces and centrifugal force is moved back and forth. The control circuits deliver a

BAD ORIGINAL OR ₁ GINALINSPECtED

Optimum flexibility in choosing the type of cycle you want, according to the timing specified for the facility. Thus, the device can be set so that it eir dom pressurized gas. Removes maximum mechanical energy or vice versa:. · ;;, - άέΐ. \ Compressed gas A maximum space of heat is withdrawn in order to optimize the facility's functionality. Air can also be used as compressed gas.

The Ρ'αο-.ί.-ΰΓΓπ will recognize that any of the above-described Aüofüh: cu;:. ~ AEF poor this invention as a Druckströr.uii.csr .-: ittöirr.aschine only used for the purpose will can veroon to mechanical energy to withdraw from a pressurized gas cnella. For such an application form., Is AVfriebsmotor C2 essentially only a starter motor. The main function of the starter motor is ά-, πη. In order to ensure that the "free piston Ci 5" is arranged in one of the outermost sections of the S-shaped pressure fluid chamber. The application of Druckströmungsn.ütcel to such an end of the S-shaped D.! uckstr ^ iuriysiv-ir.-celkamrrier C 10a causes the piston C15 _to move radially inward in the manner described above and thus impart a reaction force to the end of the cylinder C10 in order to increase the speed of the cylinder element C10 and the drive shaft C2. When a sufficient speed is reached, the starter motor C2 can be switched off or

° can be driven in an excessive speed condition to work as a generator> .. Means other than a starter motor to secure the initial positioning of piston C15 in one of the far ends of the S-shaped pressure flow Central chamber dOa are readily apparent to the person skilled in the art.

BATH ORIGINAL

While no specific embodiment of a combustion engine has been described, those skilled in the art will recognize that any of the cylinder designs described in detail above can be used as a combustion engine simply by using the inlet valves to fill a charge of combustible fuel into the pressurized fluid keiraa ·. ¹ ! - to conduct. And, if the special fuel requires a "Σ: υndi..ng, a spark plug in the end of a 0 each: pressure introduces atröirtmittelkammer and causes this to be ignited at the correct time v: -; rcifη. when the corresponding piston approaches its red position. Special occasions ^: \: ·! oj.'di.i './'. r-äri are, however, for the use of a 5 Fliokkraf tJ ^ olhenexpan 3 ion device as VerbxisierungsiroLoi "required, and these event arrangements are described in f-intr also pending application and Lc .- 'T!

BAD ORIGINAL ORIGINAL INSPECTED

lee

irseit

Claims (1)

GRÜNECKER, KINKELDEY. STOCKMAIR & PARTNER PATF-MTANWALrn ι: ιη · λ <'■ · «i'Arr.r.T ait::« i> ν ... Λ. ü ^ JME-CKKR. !> ■! ..:. I) F? H KHlKlXLItY. ηκ. ««; DI W STOCKMAlR. i «i.-i» i Of * * SCHUMANN, ι »- ι» ι f ». 11 JAKOtJ. t »> v», LJ '<Cl V. ~ - /. O \ O. t «T. CMM W t.'rJiiTCjt.t> i \ »* · H. HU. EARS. i "i» λ l3i- (»IT) ICj 9 17 8000 MÜNCHEN H2 - centrifugal force expansion method and piston expansion device claims / 1.i air cooling device characterized by the interaction of the following features: a rotatable carrier (10), a drive device ( A3) for rotating the carrier, a cylinder element (20) which forms a pressure fluid chamber (A20a), a piston element (22) which is able to cooperate with the pressurized fluid chamber, means for attaching one of the elements to the rotatable carrier a point which has a radial distance from the axis of rotation of the rotatable carrier, the centrifugal force causing a relative movement of the piston element in the pressure fluid chamber in such a direction that it reduces the volume of the pressure fluid chamber, a first Verxtileinrichtung (38) connected to the pressure fluid chamber in Connection is and only opens when the piston torque is in the position with the k l approaches the smallest volume with respect to the -Druckströ- BAD ORIGINAL medium chamber, a second valve device (21c) (which is in communication with the pressure fluid chamber and is only operable when the piston is in a position remote from that of the smallest volume with respect to the pressure fluid chamber , wherein one of the valve devices is closed every time the other Ventileinricl-.tung is open, a Raumluf t-Wärineaus exchanger (43), iT.xc continuous refrigerant channels, an XO compressor (3Ο} ,, which together with the rotatable carrier is rotatable, and a conduit device (eg, 27, 26, 2a) - around a refrigerant fluid from the second distribution device through the refrigerant fluid channels of the V7i. '. rr..äs-asca.uschers to the inlet of the compressor and voir. . ^ M9xaß to set the compressor to the first valve device in original run. 2. Air cooling device, characterized by the combination: 1. Effect of the following features: a rotatable carrier,> a drive device surr. Rotating the carrier, a Z ^ / linderelement which defines a Druckströmungsmitirelkammer, a piston element which can be brought into cooperation with the pressure fluid chamber, means for attaching the. Cylinder on the rotatable carrier at a location which has a radial distance from the axis of rotation of the rotatable carrier, the centrifugal force generating the relative movement of the piston element in the pressure fluid chamber in such a direction that the volume of the pressure fluid chamber is reduced the pressure fluid chamber is in communication and opens only when the piston element approaches the position with the smallest volume with respect to the pressure 3 ^ fluid chamber, a second valve means which is in communication with the pressure fluid chamber and opens only when the piston is remote from the position with the smallest volume in relation to the pressure fluid chamber, a room air heat exchanger with continuous refrigerant fluid channels, a compressor that can be rotated together with the rotating carrier, and a conduit device. a cold flow fluid. from the second valve device through the cold fluid channels of the heat exchanger to the inlet of the compressor and from the outlet of the compressor to the first valve device. 3. Device according to claim 1 or 2, characterized in that the first valve device comprises a check valve which is mounted in the axial end of the cylinder, a spring-loaded device which presses the check valve into the closed position, and a Batätigur? Gsschaft on the check valve, which extends into the pressure fluid chamber and yea piston element is individually engageable to open the check valve when the piston 2 ^ moves to the position with the smallest volume with respect to the pressure flow siriittelkaminer. 4. Device according to claim 1 or 2, characterized in that the heat exchanger has an arrangement of tubes which run parallel to the axis of rotation and rotate together with the rotatable carrier, and that the tubes form the cold flow channels. 5. Device according to claim 1 or 2, characterized in that the rotating carrier is attached to a hollow shaft, and that the bore of the hollow shaft forms part of the line device. BATH ORIGINAL? * -:: ··: ·; ϊ. : 33333/6 · * ■ 6. Kin rich Lung neich claim 1 or 2, characterized in that the carrier has a pair of axially spaced plates which are attached to a rotatable shaft, and that the cylinder and piston elements between the plates are attached. 7,; V.; ftcooling device, characterized by the addition.; Nv.-vvirkung of the following features: a -;., R ί rehung mounted hollow shaft, a on the 10th shaft:. ^. Rr; ei?. Single rotation attached carrier, a .'V.rdrive device for rotating the shaft, several, interacting piston and cylinder elements, which are attached to the carrier in an arrangement with equal distances around the Dv-Hachse, each cylinder element bilÜG ... one. Pressure fluid chamber in which the javraiiiye piston element is displaceable by centrifugal force in such a direction that it the volume αϊ-; Pressure fluid chamber reduced in size, a first valve direction, which came with the pressure fluid "4 ^ ';; -.-"> , a second valve device which is in communication with each pressurized fluid chamber and only opens when the respective piston is removed from the position with the smallest volume with respect to the pressurized fluid chamber, a room air heat exchanger with continuous refrigerant fluid channels, a compressor that communicates with the Hollow shaft is rotatable together ^ and conduit means for circulating refrigerant fluid from each of the pressurized fluid chambers through the second valve means, through the refrigerant fluid passages, through the bore in the hollow shaft and to the inlet of the compressor, and from the outlet of the compressor to each of the first valve devices and through the first valve means to the pressurized fluid chambers. BAD ORIGINAL Ι 8. Device according to claim 7, characterized in that each first valve device comprises a check valve which is mounted in the axial end of the respective cylinder, a resilient device which presses the check valve into the closed position, and an actuating shaft on the check valve ^ which extends into the pressure fluid chamber and is brought into engagement with the respective piston at t in order to open the check valve when the respective piston moves into its position with the smallest volume with respect to the pressure flow belt chamber. 9c device according to claim 7, characterized in that the heat exchanger has an arrangement of tubes which are arranged parallel to the axis of rotation and rotatable together with the rotatable carrier. 20 ΙΟ. Device according to Claim 7, characterized in that the carrier has a pair of axially spaced plates which are fastened to the hollow shaft, and in that the cylinder and piston elements are mounted between the plates. 11. Device according to claim 7, characterized in that the room air heat exchanger on one axial side of the carrier and the compressor are arranged on the opposite side, 12. Device according to claim 7, characterized in that a plurality of interacting piston and cylinder elements two Pairs of two elements diametrically opposed to each other with respect to the 3-axis of rotation comprise that means bind the piston elements of each pair for common movement in the respective cylinders, and that the first valve unit comprises a pair of timing valves which, depending on the Linear movements of the pair of pistons are operable, each timing valve being connected in series with the conduit means to st'i the application of pressurized fluid from the compressor at a corresponding pair of cylinders ;; rnf wherein the pistons of one pair with a :: 5ha sen displacement of 180 ° with-.üglich the piston dfc , y cnoifereri couple to be moved. 13. i / .iftkuhlungseinrichtung, characterized by the isusaru ^ uvrirkung of the following features: a sar rotation mounted hollow shaft, a on the shaft ro.r common rotation fixed support, a drive device for rotating the shaft, a pair of cylinders attached to each other on the support are mounted diametrically opposite and each limit cylindrical flow-irigsiiiitteldruckkammern, which have axes which are opposite to the axis of rotation of the carrier of a; Hadial spacing, a pair of pistons, each of which can be brought into cooperation with the cylinders and are movable by centrifugal force, to eiii the volume in the respective pressure fluid chambers. To reduce the minimum, an annular Kurbeihaitarurig, which is rotatably mounted on the hollow shaft, a p £ .ar crank arms which are attached to the annular crank bracket, connecting rod devices that connect the crank arms to the pistons, the circular crank bracket by the Reciprocating motion of the pistons is set in an oscillatory motion, a first fluid valve which can only be brought into an open position by the annular crank holder when the piston approaches the position with the smallest 3 ^ volume, a second fluid valve, which through The ring-shaped crank holder can only be brought into an open position when the pistons move from their position with the largest volume in BADORIGINAL those with the smallest volume and the first valve remains in a closed position, a room air heat exchange device with continuous coolant flow channels, a compressor who shared with the hollow shaft is rotatable, as well as conduit means to the refrigerant fluid from each of the pressure chambers through the second valve, through the refrigerant channels and through the bore of the hollow shaft to the inlet of the compressor, and from the outlet of the compressor to the first valve and through the first valve into the Circulating pressurized fluid. Arr.srn i 14. Device according to claim 13, characterized in that the heat exchanger comprises an arrangement of tubes which are parallel to the axis of rotation and can be rotated with the rotatable carrier, and that the tubes form the cold flow channels ... 20, 15. Driven tang according to claim 13, characterized in that - the carrier has a pair of plates arranged at a center distance, which are fastened to the hollow shaft, and in that the cylinder and piston elements are attached between the plates. 16. Air cooling device, characterized by the interaction of the following features: a hollow shaft which is mounted for rotation, a drive device for rotating the hollow shaft, a first carrier which is attached to the shaft for common rotation, a pair of first cylinders, which are attached to the first Carriers are mounted diametrically opposite one another and each form a first pressure flow medium chamber, the axes of which have a radial distance from the axis of rotation of the first carrier, a Pe. ar first pistons, each of which can be brought into cooperation with the cylinders and are movable by —οι I'Michkiaf t, in order to reduce the volume of the respective pressure fluid chambers to a minimum, a first, circular ring-shaped crank bracket, which is rotatably mounted on the hollow shaft , a pair of ex-ster crank arms, which are attached to the annular crank shaft, connecting rod assemblies, each providing a connection between the he? cerium. Establish crank arms and the first piston, -.-.- obai the extreme crank holder by the "back and forth movement is set in an oscillatory motion: is, a first fluid valve, the thirh r ^ oprst crank holder is operated so that it only opens when the pistons approach the position with de:? h. ei-ristan volume, a second flow mir.te'i.r.rc:. '; Il, which is so actuated by the first annular crank handle that it only opens when the pistons move out of their positions of the greatest volume, move to the position with the smallest volume before the first valve is closed, a room-air heat exchanger with continuous cold flow: r: jrc '; 5no Hollow shaft to the inlet of the Compressor and from the outlet of the compressor to the first valve and through the first valve to the pressurized fluid kairenern, a second carrier mounted on the hollow shaft for common rotation, a pair of second cylinders mounted on the second carrier diametrically opposite each other and each form second pressurized fluid chambers, the axes of which are radially spaced from the ° axis of rotation of the second carrier, a pair of second pistons which each cooperate with the second cylinder and are movable by centrifugal force to the volume of the respective BAD ORiGfNAL _ ΟΙ pressurized fluid chambers To reduce the minimum, a second, annular crank bracket, which is rotatably attached to the hollow shaft, - a pair of second crank arms which are attached to the second, annular crank bracket, connecting rod devices, which each have a connection between the second crank arms and the make a second piston, the second annular crank bracket is set in an oscillating motion by the reciprocating motion of the wide pistons, a third fluid valve, the ^. is operated by the second annular crank holder so that it opens only when the second pistons approach the position with the smallest volume, a fourth flow control valve, which is operable by the circular crank holder so that e; -; opens only when the second pistons move from their positions with the greatest volume to their positions with the smallest volume and the third flow control valve is closed, and a conduit means to circulate the refrigerant from each of the second chambers through the fourth valve, through the refrigerant: s -:.: "c5ir.mittelkanäle and through the bore of the hollow shaft to the inlet of the compressor and from the outlet of the compressor to the third valve and through this third valve to the second fluid chambers in one circulation. 17. Cooling device according to claim 1, 2 , 7, 10, 12 or 13, characterized in that each cylinder has an inlet channel for receiving hot compressed gas and an outlet channel for discharging cooled, expanded gas as well as a heat insulating device which separates the channels. 35: "V: Γ · ·: -Γ :. ": 33 333 -ιο-ι 18. Device according to claim Τ6, characterized in that the heat exchanger has an arrangement of tubes parallel to the Drehac Has hse and rotatable with the rotatable body, which form the cold flow inlet channels. 19. '-iT / nricntung according to claim 16, characterized in that each carrier has a pair of axial spacing angec.ic' ;; - iv.sr plates attached to the hollow shaft bef efe-.L-; r?> ind, and that the respective cylinder and piston neli-iiierite are mounted in the plates. 20. LuI: ti; jhlungseinrichtung, characterized by the Z "j.iianüi '; effect of the following features: a--:; shaft attached for rotation, - a drive device for rotating the shaft, a first and a second group.- uüs one Number of interacting piston and cylinder elements, which are mounted on the shaft in an arrangement with intervals around the axis of rotation, the first group being axially spaced from the second group, each cylinder element forming one Pressure fluid chamber in which the respective piston element is displaceable by centrifugal force in a direction to reduce the volume of the Drackströr.rangsmittelkammer, a first valve device which is connected to each pressure flow smitteikkammer the first group and only opens when the respective piston elements are in position with the smallest volume approaching the pressurized fluid chambers, means for venting each pressurized fluid came mer of the first and second groups only when the respective pistons are removed from the position with the smallest volume with respect to the pressure fluid chamber, a second valve device which is in communication with each pressure fluid chamber of the second group, a device which is responsive to the movement of the first piston group responds, BADORIGINAL • A «ft ** to control the opening of the second valve device, wherein the first and second valve device are operated sequentially, and means for supplying pressure fluid to the first and second valve device / wherein the pistons of the first group qeqen above the excitation the pistons of the second group are phacenically offset. 21 = Lufttruhlungseinrichtu.ng, characterized by the Zu ^ e-HuUt = :: effective of the following features: a hollow shaft attached for rotation, a drive shaft, a first and second group of several, cooperating piston and Eylxru ^ r-ile.v.snten, which are attached to the shaft in an arrangement irtit gieiche-πι distance around the axis of rotation. 7; although the first group is axially spaced apart from the second group, each cylinder element forms a pressure fluid chamber in which the respective piston can be displaced by centrifugal force in a direction zai.'i reducing the volume of the pressure flow device karaiuv.r, a first valve device, clie communicates with each pressurized fluid chamber of the first group and only opens when the respective piston elements change their position with the smallest. Volume with respect to the pressure fluid chambers approach, means for venting the pressure fluid chambers of the first and second groups. which opens only when the respective pistons are removed from the lowest volume position with respect to the 3C pressure fluid chamber, second valve means communicating with each pressure fluid chamber of the first group, means responsive to the movement of the first group of pistons responds to control the opening of the second valve means, the first and second valve means having been actuated sequentially, means for supplying pressurized fluid to the first and second valve means, the BAD ORIGINAL pistons of the first group being out of phase with the excitation of the pistons of the The second group is energized, a room air heat exchanger which is installed on the hollow shaft and has continuous cold flow channels, a compressor which can be rotated together with the hollow shaft, and a conduit line to pass a cold flow medium from each of the pressure chambers the second outlet device through άχ'Ά refrigerant flow channels and through the tube of the hollow shaft to the inlet of the compressor soXiie from the ·. Outlet of the compressor to the first and second vent. LI device and through the first and second VantI device to the first and second group of pressure flow srnittelkainmern to circulate. 22. Device according to claim 21, characterized in that the heat exchanger has an arrangement of pax a χ 3 'nl. sui: the axis of rotation and rotatable tubes together with the rotatable shaft, which form the Käj. ^ e-Jtroiamittelkanäle. 23. Device according to claim 20 or 21, characterized7 that the first valve device comprises a check valve which is mounted in the axial end of the cylinder, a resilient device that pushes the check valve in the closed position, and an actuating plunger on the check valve, which is in the Pressurized fluid chamber extends into it and is engageable with the piston element to open the check valve when the piston moves into its smallest volume position with respect to the pressurized fluid chamber. 24. Air cooling device, characterized by the interaction of the following features: a rotatable carrier, a drive device for rotating the carrier, a cylinder element which forms a BAD ORIGINAL -13- pressure separating medium chamber, a piston element which cooperates with the pressure flow medium chamber, a device for attaching a of the elements, on the rotatable carrier in a position with a radial distance from the axis of rotation of the rotatable carrier, wherein centrifugal force produces a relative movement of the piston element in the pressure fluid chamber in a direction to reduce the volume of the pressure fluid chamber, a first valve device which, with the pressure ^ t "; cT: ur.gsmittelkamrner is in connection and r.ur 0.2.Τ.ΪΪ opens when the piston element of the St3lJv -: / K, with the smallest volume related] .i the pressure" straruc: "^; oinitte! chamber approaches, a second valve inlet, t'ci :; j. which is in communication with the pressurized flow medium chamber and only then opens when the piston is removed from the ci-r position with the smallest volume with respect to the pressure fluid chamber, one of the valve means is closed every time the other valve means is open, a .Ver Kompressor, which is rotatable together with the hollow body i & t. a first conduit means which is rotatable together itd.-t cierri Kcrj-r to direct air from the second valve means into a chamber to be cooled., and a second conduit means to convey air from the chamber to the inlet of the compressor and from the To direct the outlet of the compressor to the first valve device. 2-5 device according to claim 24, characterized in that the first valve device comprises a check valve which is mounted in the axial end of the cylinder, a resilient device which presses the check valve in the closed position, and an actuating tappet on the check valve, which is located extends into the pressure flow medium chamber and can be brought into engagement with the piston element in order to open the check valve when the piston moves into its position with the smallest volume in relation to the pressure flow medium chamber. 26. Device according to claim 24 marked * - characterized in that the rotating carrier is attached to a hollow shaft and that the bore of the hollow shaft forms part of the second line device. 27. Device according to claim 24, characterized in that the chamber is a space and that the entire device, with the exception of parts of the first and second conduit means, is mounted outside the space. Device according to claim 24, characterized in that the first conduit device ends in diffuser nozzles which rotate within the chamber. 29, air cooling device for a room with a ceiling. · Characterized by the interaction of the following features: a; jur rotation about a vertical axis above an opening in the ceiling, a support, - which is attached to the shaft for common rotation is, a drive device for rotating the shaft, several interacting piston and cylinder elements =, which are attached to the carrier in an arrangement with even distances around the axis of rotation, each cylinder element forms a Druckströmungsi: iittelkammer in which the respective piston element is displaceable by centrifugal force in a direction to reduce the volume of the pressurized fluid chamber, a first valve device which is in communication with each pressurized fluid chamber and only opens when the respective piston element approaches the position with the smallest volume with respect to the pressurized fluid chamber, a second valve device, with every pressure k-flow is connected to the smi ttelkammer and only then BAD ORIGINAL An "**» i> ft * * · β »Aft * * · · ♦ rt Λ λ η« * # * * · -15- opens when the respective piston of its position with the smallest volume with respect to the pressure flow medium chamber is removed, a compressor which is rotatable together with the hollow shaft, a first line device, which can be presented together with the hollow shaft, the first line device is rotatable with the door, qer to remove air each pressure fluid- ka: .-.:? er: through the second valve means and from there .Ir; to direct the room through the opening in the ceiling and a second conduit device, which includes the bore of the hollow shaft, in order to supply room air to the inlet of the compressor, from the outlet of the compressor to each first valve device and through the first valve device to the pressure flow medium chambers steer * 30, device according to claim 29, characterized in that the first conduit device ends in diffuser nozzles which rotate within the room near the ceiling. 31, method for extracting heat from a compressed gas, characterized by the following steps: 1.} Erection of a cylinder and piston assembly an axis which is spaced apart from the path of the relative movement of the piston and cylinder and runs transversely thereto, the centrifugal force relative to the piston in an end position pushes the cylinder, "- 2.) Introducing a pressurized gas filling into the cylinder, which is sufficient to move the piston and cylinder relative to one another into the other end position against the effect of centrifugal force, whereby the gas expands and cools and the rotational speed of ^ ⁵ piston and cylinder increases, 3.) removing the cooled and expanded gas from the cylinders and passing the gas through a heat exchanger to reheat it, and BATH ti 1! ¹ S ¹ S Λ / ΓΛ WWVVV * " -16- ■. " 4.) Compress the reheated gas for renewed Introduce into the cylinder. 32. The method according to claim 31, characterized in: gekennzeichr.vrt; that the compressed gas comprises air. 33. Process for cooling a room by means of pressurized gas, characterized by the following steps: .) Oreru: r: a cylinder and piston arrangement outside the space around an axis which is at a distance from the path of the relative movement of piston and cylinder and extends transversely to this / whereby the centrifugal force pushes the piston io. Eir.e end position with respect to the cylinder presses, 2.) .t-irilo-: ten a compressed gas filling in the cylinder, which is sufficient to move the piston and cylinder relatively close to the other end position against the effect of centrifugal force, whereby the air expands and cools and the speed of rotation of the piston and cylinder increases, 3.} Er.trerpen the cooled and expanded air ϊΐυ, Β dent. Cylinder and introducing air into the room urd
.) -Bntnehr.er. of air from the room and compressing this air for reintroduction into the cylinder. 34. Ve. "F their for cooling a room with compressed air, characterized by the following steps: 1.) Erection of a cylinder and piston assembly outside of the space around an axis that is opposite to the path of the relative movement of the piston and cylinder has a distance and extends transversely thereto, wherein the centrifugal force moves the piston into a Pushes the end position with respect to the cylinder, 2.) Introducing a compressed air charge into the. Cylinder, that for a relative movement of the piston and cylinder in the other end position against the effect centrifugal force is sufficient, whereby the air expands, BATH -ΠΙ cools and the speed of rotation of pistons and cylinder increased,
3.) Remove the cooled and expanded. air out of your cylinder and introducing this air in the room through a line that is shared with the.:. Cylinder rotates and in a diffuser nozzle enüet, which rotates within space, and 4.) Extracting air from the room and compressing it this air to be reintroduced into the cylinder. 35. Device for extracting heat and mechanical jiier-gio from a pressurized gas, characterized by the following features: '
eir Txi.qex. which is rotatable about an axis, a drive means for rotating the carrier, a plurality of cylinder elements attached to the rotating carrier in an arrangement with the same distances around the axis, each cylinder element forms an elongated fluid chamber, a free piston is in Longitudinal direction in each pressure flow direction. "Chamber movable, the cylinder elements are attached to the öx-:" ^: '-jjaron support, the movement sv / eg of each piston extending from a position near the axis to a position remote from the axis, whereby Centrifugal force moves the free piston into the distant position, an inlet valve device which establishes a connection between a source of compressed gas and the distal end of each cylinder element, a device for opening the inlet valve device only when the free pistons approach the respective off-axis positions, to receive a charge of pressurized gas in the respective pressurized fluid chambers, and exhaust valves i Devices which are each connected to the pressurized fluid chambers and can only be operated when the free pistons are approaching their respective positions close to the axis, each pressurized gas charge increasing the rotational speed of the carrier and in a cooled, expanded state BATH ORIGINAL fr · y y y-y y / 1> -18 state is issued. 36. Device according to claim 35, characterized in that that the free piston comprises a container which is filled with a metal from a group of heavy metals filled, which include lead and mercury. 37. Execution according to claim 35, characterized in that that the free piston on its outside is coated with an organic plastic, which has lubricating and sealing properties. 38. LIa η direction according to Ansoruch 35, thereby marked, that the cylinder elements have a curved configuration in the longitudinal direction. 30. Device according to claim 35, characterized in that that the pressurized fluid arms one have a uniformly circular cross-section so -ie a gCj-: rüftimte longitudinal axis, and that the free piston with its outer formation includes a ball. 40. Device according to claim 35, characterized * indicates that the Druckströmumgsmittelkammern one uniformly circular cross-section and one curved Have longitudinal axis, and that the free piston has the outer shape of an ellipsoid, wherein the smaller diameter of the ellipsoid essentially equal to the inside diameter, but smaller than is the inner diameter of the pressure flow center chamber. 41. A device according to claim 35, characterized ^ characterized marked ³ in that the pressure fluid chambers have a curved form in the longitudinal direction and in that the axially far proximal end of each pressure flow is smittelkammer formed by a wall, ORIGINlALiNSPECTED ^ ORIGINAL nan *> ■ ⁿ -19- which is arranged in a generally radial plane with respect to the axis of rotation. 42. Device according to claim 35, 36 or 37, characterized in that the longitudinal axis of each Druckströmraur.qsmittelkammer forms a spiral VJeg which lies in a single plane. 43- Τ. ·. ·.: · .Direction according to claim 35, 36 or 37, characterized in that XO yc / .eju., Ν jchn ^ -t; that the longitudinal axis of the ^{pressurized fluid 1} -:.: ^^ - forms a helical / spiral path, Xvobe .. '. Λ,:. s radially outer end of Druckströrnungsmittelkar.rvir ct-ncn is axially offset from the inner end. , 44. liinrichfcung according to claim 35, characterized in that Ü3.3 the rotating support comprises two plates, the ar-sinander are attached, and that the 2yli "ii5erel · '-.nente through adjacent recesses are formed, which are formed in the contact surfaces of the: -Istten. 45. E J. η r I do g according to claim 35, characterized in that that the inlet valve device is a check valve includes, in the radially outer end, one attached to each pressurized fluid chamber is a resilient device that controls the check valve pushes into the closed position, as well as an actuating shaft on the check valve extending into the pressurized fluid chamber and with the respective free piston is engageable to open the check valve when the free piston moved to its remote location. 46. Device according to claim 35, characterized in that the valve device is a check valve which is mounted in the radially outer end of each pressurized flow medium chamber, a resilient one Einrichturg that the check valve in a closed position pushes an actuating stem on the check valve, which extends into the pressure fluid karemer extends into it and is engageable with the respective free piston to the Rückschlr.igventil to open when the free piston moved to the remote position, as well as an adjustable timing device to prevent the return of the To delay the non-return valve in the closed position, changing the amount of pressurized gas admitted into the pressurized fluid chamber. 47. Bitir i.-rung myself to claim 35, further characterized dv-.rch a ^ n room air heat exchanger with fluid -Through channels, a compressor that gerueinsa ;;; rrtit the hollow carrier is rotatable, as well a L-3.it;. ". rig3e.device that removes the cooled gas from the AusIaSv-iiitiloi,! Direction through the flow channels of the U-i.rrf.eaa stau shear s into the inlet of the compressor and from the outlet of the compressor into the inlet valve means heads in one round. 48. Eirriehtung according to claim 35, - characterized in that that the compressed gas includes air, and further characterized by a line device for Connecting the exhaust vexa ti! Device to a to cooling liammer. 49. Device according to claim 35, characterized in that the compressed gas comprises air, and further ° ® characterized by a line device for connecting the exhaust valve to the chamber to be cooled, a rotating compressor which can be rotated together with the rotating carrier, and a second line device to connect the chamber to the inlet of the ^Ov - rotary compressor and to connect the outlet of the rotary compressor to the fluid inlet valve. : BAD ORIGINAL ORIGiNALlNSPECTED Ä * fe * «* * 4 * -Φ * ♦ -21- 50. Device for extracting heat and mechanical Energy from a compressed gas, characterized by the following features: a carrier rotatable about an axis, a drive device to rotate the carrier, several cylinders i.:.-STi■::_■ :. those on the rotating carrier in an arrangement with equal spacing around the. Axis are attached, each Z \ I.inaereiemerit forms an elongated Druckströniuiicfsrciittelkammer, a free piston, which in longitudinal _: Direction .Ir: each pressurized fluid chamber movable is ... the cylinder elements: are on the rotating body attached ^ being the path of movement of each free Piston extends from a position close to the axis to a position remote from the axis, and the centrifugal force the freer ·. Piston moved to the off-axis position, an inlet valve device that connects between a pressure; -asguelle and the end of a distant axis every. 2ylxndere.leme.nts manufactures a facility to open the inlet valve device only when all free pistons have reached the positions remote from the axis, um <j3i;! s ..-. ir! 3c; rr, a pressurized gas filling in the respective To receive pressure fluid chambers, and a Äbyap ^ valve device that connects to the respective Druckströmungsrnittelkammern produces and opens only when the respective free piston approaches the near-axis position, whereby the free Pistons are moved substantially synchronously in response to each compressed gas charge. 51. Device according to claim 50, characterized in that the cylinder elements one in the longitudinal direction have curved training. , 52. Device according to claim 50, further characterized by having a room air heat exchanger Fluid passage channels, a compressor which is rotatable together with the carrier, and a Line device for making a circuit BATH ORIGINAL cooled gas from the vent valve means the fluid channels of the heat exchanger to the inlet of the compressor, as well as from the outlet of the compressor to the inlet valve device. 53. Device according to claim 50, characterized in that the compressed gas comprises air, and furthermore characterized by a line device for connecting .the exhaust valve device to the cooling chamber. 54. Device according to claim 50, characterized in., that the compressed gas comprises air / and further drawn by a line device to Connecting the exhaust valve device to the chamber to be cooled, a rotating compressor, the commonEc-iiu is rotatable with the rotating carrier, sow3'c- eirxa second line device for connection the K ν natter to the inlet of the rotating compressor ^ O as well as de :: outlet of the rotating compressor the Strc fluid inlet valve means. 55. Device for extracting heat, and mechanical Energy from a compressed gas, characterized by the following features: a carrier rotatable in one axis, a drive device sum rotation of the beam, several cylinder elements, which are attached to the rotating support in an arrangement rotating around the axis at equal intervals each cylinder element forms an elongated pressurized fluid chamber, a free, .. Piston running longitudinally in each pressurized fluid chamber is movable, the cylinder elements are rotatable. Attached, the loading The path of travel of each free piston extends from a position close to the axis to a position remote from the axis, whereby the centrifugal force moves the free piston into the off-axis position, an inlet valve BATH ORIGINAL ORIGINAL INSPECTED -23- Direction, which establishes a connection between a pressurized gas source and the end of each cylinder element remote from the axis, a measuring device on each of the cylinder elements for determining the presence of the respective piston in the position remote from and close to the axis, a device which responds to the measuring device ar ?, the -Einlaßventileinrichtung only be open; when all the free piston have reached the off-axis plies to jointly take a charge of compressed gas in de χ respective pressure fluid chamber, and a drain valve device, each with the Dr-acks ^ römungsinittelkammern in conjunction stands, as well as one Sir, direction, which corresponds to the measuring device, u. ^v n Ό. ¹ -. _-- l :: - :: as \ rentileinrichtung only to open when the f.ve.i.an pistons are each approaching their position close to the axis, whereby the free pistons move essentially synchronously depending on the pressurized gas fillings . 56. Apparatus according to claim 55, characterized in ₇ - that the pressurized gas comprises air, and further characterized by conduit means for connecting said exhaust valve means to a chamber to be cooled. 57. Device according to claim 55, characterized in that the compressed gas comprises air, and further characterized by a device for connecting the exhaust valve device to a chamber to be cooled, a rotating compressor, which can be rotated together with the rotating carrier, as well as a second conduit device, around the chamber to the inlet of the rotating compressor as well as the outlet of the rotating To connect the compressor to the fluid inlet device. BATH :.: "^ YYY a J / -24- 58. Device for extracting heat and mechanical Energy from a compressed gas, characterized by the following features: a carrier which is rotatable about an axis, a drive device for rotating the carrier, several cylinder elements that are attached to the rotating carrier in one Arrangement are fixed at equal intervals around the axis, each cylinder element forms an elongated Pressurized fluid chamber, a free piston, the .vi longitudinal direction in each pressurized fluid— ■ chamber is movable, the cylinder elements are on rotatable carrier attached, the path of movement of each free piston differs from a near-axis La ^ -i; SU extends in an off-axis position, and where the centrifugal force moves the free piston into the off-axis position - an inlet valve device that has a Print size source and the off-axis end of each Zyj-indareXav.cnts connects, an exhaust valveeiiirichtv.r.g, ciie to the pressurized fluid chambers, respectively is connected, a first measuring device to jedeui ZyI ir. The element, - to the presence of the respective to determine free Kc "Lbens in the off-axis position, a second measuring device on each cylinder element, to the presence of the respective free piston in a middle position between the off-axis and the to determine the near-axis position, a third measuring device on each cylinder element to ensure the presence of the respective free .; Piston in the position close to the axle determine a facility that is on the operation all first measuring devices responds to simultaneously to close all exhaust valve devices and to open all inlet valve devices to to initiate the pressurized gas filling in all fluid pressure chambers, a device which is based on the second 3 ^ measuring devices responds to each of the inlet valve devices to close, and means responsive to the third measuring means to to open each of the drain valve devices, wherein BAD ORIGINAL ORIGINAL INSPECTED the free pistons essentially synchronously through the Druckgaslaäungen are moved. 59. Device according to claim 58, characterized gekennzeichnebdaß the compressed gas comprises air, and also ge] '; er.-nr.-ic'h..iet through a line device to the Connect the exhaust valve devices to a too cool in the other chamber. 60. EEnrichLung according to claim 58, characterized thereby. äaJ3 the pressurized gas comprises air, and further gekK-ii "iilehnet by conduit means to the .'b ^ ivsveritileinrichtungen with the to be cooled Ka'.TK · r .- zxx connect a rotary compressor, de.t .je?: : i € .ia £ .arn is rotatable with the rotating carrier, as is a second conduit device to the chambers with associate. 61. method for operating a device for generating heat and mechanical energy from a compressed gas by a plurality of diametrically opposed cylinder elements that rotate around an axis and each form pressure fluid chambers that extend from a point remote from the axis to a position close to the axis, wherein the cylinders are each free piston, an inlet valve which communicates with a Druckströmungsrnittelwelle in connection, and a ^ou outlet for cooled fluid comprise, characterized by the following steps: 1) measuring the position of each free piston when it is off-axis and approaches near-axis ends of the pressurized fluid chamber, 2.) simultaneous closing of the exhaust valves and opening of the intake valves two diametrically opposed to each other opposite cylinder elements if the respective free piston elements both the axially BATH ORIGINAL far end of the respective pressurized fluid reach chamber, and
3.) open the outlet valve of each cylinder when the respective free piston reaches the near-axis end of the pressure fluid chambers, the free pistons of the diametrically opposite one another. Cylinders move essentially synchronously with one another. ¹ ^ 6 2 .. Ancestors of operating a device for extracting heat and mechanical energy from a compressed gas darch several diametrically opposite one another; · ^; β cylinder elements, which rotate about an axis and ^ civ / eils pressure fluid chambers, which extend 1 ¹ ^ Sixci-x vou a point remote from the axis to an axially located position, the cylinders each free Koibfc-i, - an inlet valve, which with a Druckströnmrigsx-iitfceiyuelle in connection, as well as an Aus ^ - laBventil for cooled, expanded fluid ^Ayj urr: i: ': T. "= r. characterized by the following steps: 1.) £ i-3sfiexi the position of each free Piston, if he lies between the end-vr- of the respective pressure fluid chamber distant from the axis and the end-vr- close to the axis, 2.) timely closing of the exhaust valves and Opening the inlet valves of two diametrically opposed cylinder elements when the two respective free piston elements the off-axis ends of the respective pressure flow have reached Mittelkaramern, 3.) Close the inlet valves when the respective pistons are in a middle position between the axles and off-axis ends of the pressurized fluid chambers have reached, and 4.) open the exhaust valves of each cylinder when the respective free piston reaches the end near the axis has reached the pressure fluid chambers, the free pistons of the diametrically opposed BAD ORIGINAL ORIGINAL INSPECTED lying cylinders move essentially synchronously. 63. A method of operating a device for extracting heat and mechanical energy from a J: return gas through a plurality of cylinder elements, which in order to; j-.cn se rotate and each pressure flow effiii.tel ;; 2r.u: iern form, which extend from an off-axis Pur'-t zn a position close to the axis, the S-ylindar each having a free piston, an inlet valve, du , "is in communication with a source of pressurized fluid and includes a chilled fluid discharge valve characterized by the following steps: -j, } ;: -; -: <: sev, the position of each free piston when it approaches the off-axis and near-axis ends of the pressure flow medium channels, 2.) simultaneous closing of the outlet valves υιό open the inlet valves of all cylinders, if all the free pistons are the ends remote from the axis the pressurized fluid chimneys reached habon, \: md 3.) opener of the exhaust valve of each cylinder, v / e.ix: the respective free "piston, the end near the axis of the pressurized fluid chamber with the free pistons moving substantially synchronously. 64. A method of operating a device for extracting heat and mechanical energy from a Pressurized gas through several cylinder elements that rotate about an axis and each chamber pressurized fluid form that extend from an off-axis point to a extend near the axis, the cylinder each free piston, an inlet valve with a Source of pressurized fluid in communication, and comprise a cooled fluid outlet valve, marked you: ch the following steps: _B AD -2 δ-1.) Masses of the location of each free piston if it approaches the off-axis and near-axis ends of the pressure fluid chambers, 2.) Simultaneous closing of the exhaust valve and opening of the intake valve of all cylinders, if all free piston in each case the off-axis ends of the Pressurized fluid chambers have reached 3.} Close the inlet valves when the respective Piston a middle position between the axially and off-axis ends of the pressurized fluid chambers have achieved, and 4.) opener «of the exhaust valve of each cylinder, if the respective free piston is aligned Has reached the end of a pressure chamber, this IB moving more freely: Pistons move essentially synchronously. 65. Device for extracting heat and mechanical Kne- rgi '^ from a pressurized gas, characterized by the additional effect of the following features: a rotating carrier, a drive device for turning, ο.ί- ·: ■. A carrier about a first axis, a cylinder device tang that has an elongated fluid chamber that has a generally S-shaped longitudinal axis _? a device for rigidly attaching the ZyI inci sr device to the carrier, wherein the ends of the pressure flow center chamber are arranged on the opposite sides of the first axis and off-axis in the radial direction, while the middle sections of the pressure flow chamber are close to the first axis. ^ O lay, a free piston that sits in the pressurized fluid kaiamer attached for sliding and sealing movement due to its S-shaped length extension is, first and second valve means around the ends of the pressurized fluid chamber, respectively To supply compressed gas, a third and fourth valve device to each expanded gas from the Drain ends of the pressurized fluid chamber, as well as several piston gauges spaced longitudinally BAD ORIGINAL ORIGINAL INSPECTED -29- the length extension of the cylinder device and operatively associated with the first, second, third and fourth valve means. Bind to causing the plunger to constantly move away from one end g the pressure fluid cam to the other · and to move forward when the carrier is rotated. 66. Device according to claim 1 and 65, characterized in that the free Kolbon a container nm.- - ^ q fa £ t, the gefü- with a heavy metal from a group It is. which includes lead and mercury. 67. Device according to claim 1 and 6 5 ,, thereby ge-ker ..- :. 2C: ichii3t, that the free piston is coated on the outside with an organic plastic, the has sharp circular and sealing properties. 6S. Device according to claims Ί and 65, characterized in that the piston measuring device responds magnetically and the piston has a permanent magnet U- ¹ U ei .0, - - 69. Device according to Claims 1 and 65, characterized in that that the S-shaped pressurized fluid chamber has a uniformly circular cross-section and that the piston comprises a ball. 70. Device according to Claim 1 and 65, characterized in that that the S-shaped pressure fluid SO chamber has a uniformly circular cross-section and that the free piston comprises an ellipsoid, with one that merges with the smaller axis Diameter which is substantially the same as, but less than, the diameter of the pressurized fluid chamber. BATH 71. Kinrichtuny according to claim 65, 66, 67, 68, 69 odor 70, characterized in that the one another diametrically opposed end walls of the S-shaped pressurized fluid chamber each "in an im are arranged substantially radial plane with respect to the axis of rotation. 72. Device according to claim 65, characterized in that two of the piston measuring devices are each arranged at the outer ends of the S-shaped Druckströmungism.ittelkaiiiraer and each open the adjacent first and second Ventileinrichc.uaj cause when the piston approaches one of the Au 3 en c ν, /. le.α of the S-shaped pressure fluid chamber r t. 73. Device according to claim 65, characterized in that dctß two of the piston measuring devices each near the outer ends of the S-shaped pressure flowKmittelkc .-- imer are arranged and it jev / eils. ■; / ewe ;; en, - that of the adjacent first or second Valve device one as well as one with diametrical distance arranged third and fourth valve device opens when the piston approaches one of the outer ends The S-shaped pressure fluid chamber approximates that one: third and fourth piston gauges, respectively I-: '. ~ Igs of the middle section of the S-shaped Pressure fluid chamber is arranged, wherein the third piston measuring device on the piston movement 3Q in one direction and the fourth piston gauge responsive to piston movement in the opposite direction to that of the first and second valves to close the open to allow expansion of the pressurized gas that drives the piston. BATH ORIGINAL ORIGINAL INSPECTED -31- 74. Luftkühlungaeinrichtung, characterized by the interaction of the following features: a rotatable carrier, a drive device for rotating the carrier about a first axis, a cylinder device, which srnittelkairmier an elongated pressure flow forms, which has a generally S-shaped length, a device for rigid attachment of the cylinder device on the carrier, the ends of the pressurized fluid chambers at the opposite ends. Sides of the first axis and, seen in radial Rieb.tu * · are arranged off-axis, and the middle · = "Sections of the pressurized flow medium chambers hub ai-i-iser Achf.e are arranged, the pressure flow Kiit:. £ lkan :: r.2r has a Gleichfüraigerx along its length Cross-section on, a free piston is in do.c Druckströmungsraittelkaminer for sliding movement through their S-shaped length extension attached, one first and second valve device for each Feeding of compressed air into the ends of the pressure flows Rode into the chamber, a third and fourth valve direction for releasing the expanded air from the ends of the pressurized fluid chimneys, "voüoei Lr ^ -hrsre piston measuring devices at a distance lengthways the length extension of the cylinder device arranged and operatively connected to the first, second, third and fourth valve means To cause pistons to continuously move from one end to the other of the pressurized fluid chamber and to move forward when the carrier rotates as well Q ^ a line device for connecting the third and fourth valve means to a chamber to be cooled. 75. Device according to claim 74, characterized in that the diametrically opposite one another End walls of the S-shaped pressurized fluid chamber each in a substantially radial plane with respect to each other the rotation I se are arranged. BATH ORIGINAL 76. Luftkühlungseinrichtüng, characterized by the interaction of the following features: a rotatable carrier, a drive device for rotating the carrier about a first axis, a cylinder ind. device, the one elongated pressure flow smittelka.i.T «i3r with a generally S-shaped longitudinal axis,. a device for rigidly attaching the cylinder device on the carrier, with the ends of the pressure flow rule channels on the opposite sides • jO of the e rs ton axis as well as with, seen in the radial direction. -AchsaLetand are arranged, and the middle sections of the pressure fluid chamber are arranged close to the first axis, the pressure fluid kcir, ^r ; er · .- "■ :: Is along its length of a uniform cross-section, with a free piston, dor in the pressure fluid chamber to the Gleirbev.cgunv over its S-shaped elongation hiriv.'eg a: ·.-_: ah avenge is, a first and second valve inlet; i: .ar_9 "for the respective feeding of compressed air into the ends of the pressure fluid chamber, a third ~ ti · and fourth valve device for the respective Abis. a.ν er: oes expanded gas from the ends of the Druckbtröirtungsraittelkammer _r as well as a plurality of piston pressure devices, which are spaced along the length of the cylinder device and are operatively connected to the first, second, third and fourth valve device, around the To cause pistons to constantly move back and forth from one end of the pressure fluid chamber to the other with the rotation of the carrier, a compressor which is rotatable together with the rotatable carrier, a first conduit means, which the third and fourth valve means with a to be cooled Space connects, a second line ₍ device, which connects the space with the inlet of the compressor, and a third line device, which connects the outlet of the compressor with the first and second valve device for feeding BAD ORIGlNA ^ÖAU ORIGINAL INSPECTED -33- of compressed air into this connects. 77. Air cooling device, characterized by the combination of the following features: a rotatable carrier, a drive device for rotating the carrier about a first axis, a cylinder device which forms an elongated pressure fluid ^ arrrver with a generally S-shaped longitudinal cicliye., A Device for rigid attachment of the cylinder :: '- r _; .: - 'Äinriohtung on the carrier, whereby the end of the Druckfci - ;; ou; ungsni ttelkamme on the opposite sides are arranged on the first axis and, seen in the radial direction, with center distance, and the pixttic ~ n sections of the The first pressure browning agent can be arranged near the first axis, the pressure dropping agent chamber has a uniform cross section over its length, the piston is free of pressure in the pressure flow; ..v: ^ r. for the sliding and sealing movement xxbCiT arranged their S-shaped length extension away, one first and second valve device for the respective feeding of compressed gas into the ends of the Druckströmuri-jsinittelkammer, a third and fourth valve device for the respective discharge of the expanded gas from the ends of the Druckströmungsmi ttclkammer, a plurality of piston gauges spaced along the length of the cylinder means and operatively connected to the first, second, third and fourth valve means around the ³ ^ to cause pistons to constantly move back and forth from one end of the pressurized fluid chamber to the other end for the rotation of the carrier, a compressor which is rotatable together with the rotatable carrier, a heat exchanger for cooling one Air flow, as well as a line setup to. Directing the expanded gas from the third and fourth Ventilei direction through the heat exchanger to the inlet of the rotating compressor as well as from ORIGiNAL INSPECTED BmU ORIGINAL . * Γ. * "*,« '% · * 00000/0 Rotary compressor outlet to the first and second valve means. 78. Device according to claim 77, characterized in that that the diametrically opposed ervivrands of the S-shaped pressurized fluid camraar are each arranged in a substantially radial plane with respect to the axis of rotation. 79. Device for extracting mechanical energy from a compressed gas, characterized by the Combination of the following characteristics: ein'üia eins first axis rotatable carrier, a cylinder device, the one elongated flow means - karr.mer forms with a substantially S-shaped longitudinal axis, a device for rigid attachment the 2ylJ.ndereinrich.tung on the carrier, with the ends of the pressurized fluid chamber to the opposite Sides of the first axis as well as, in the radial direction gesehsrx, located away from this, and the I-ut celah sections of the pressure fluid chamber are arranged near the first axis, ein.freier piston sealing in the pressurized fluid chamber for sliding movement over its S-shaped length extension is arranged away, first and second valve means for the respective feeding of pressurized gas into the ends of the pressurized fluid chamber, a third and fourth valve means for releasing expanded gas from the ends of the pressure chamber, respectively, and means responsive to the location of the piston in the pressurized fluid chamber, to control the first, second, third and fourth valve means to cause the piston is constantly moving from one end to the other of the pressurized fluid chamber and that reaction forces can be generated on the cylinder in order to make the cylinder rotate around the first axis. 'BAD ORIGINAL ORIGINAL INSPECTED -3 5- 80. Device according to claim 79, characterized by that the free piston comprises a container which is selected from a group of heavy metals, which include lead and mercury, filled with one is. 81. Device according to claim 79, characterized in that it is marked. that the free piston on the outside with. ei.:Siu organic plastic is coated, which lubricating: has new and sealing properties. 82 »Device according to claim 73, characterized in that: ial: - tr- ^j :, - that the S-shaped pressure fluid cable - ..:, w. e: L ^r : on uniformly circular cross-section eiu £ ■ ", - eiSi and the piston encompasses a sphere. 83. i; üir ich do g according to claim 79, characterized in that the S-shapedc; The pressure flow means has a similarly circular cross-section and that the free piston comprises an ellipsoid, whose the minor axis coincident diameter in wc lateral equal to but smaller than the diameter of the pressure fluid chamber. 84. Device according to claim 79, 80, 81, 8 2 or 83, characterized in that the one another diametrically opposite end walls of the S-shaped pressurized fluid chamber each in an im are arranged substantially radial plane with respect to the axis of rotation. 85. Device for extracting heat and mechanical energy from a compressed gas, characterized by the interaction of the following features: ° a carrier rotatable about a first axis, a cylinder device, which is an elongated pressurized fluid chamber with a generally S-shaped longitudinal axis, means for rigidly attaching the BATH ORIGINAL ι <■ * ο ο α ο j / υ -3 δ-cylinder device on the carrier, the ends of the Drucks tröniemittelkammer to the. opposite sides of the first axis and, viewed in the radial direction, spaced therefrom, and the central portions of the pressurized fluid chamber are close to the first axis, a free piston which "is in the pressurized fluid chamber for sliding, sealing movement over its S-shaped length- Extension is attached, a first and a second valve device to feed compressed gas into the respective end of the DiTjckströmemittelkammer: a third and fourth valve device to expand gas also dam the respective end of the pressure fluid-] ςετ.τ; Γι · 3Γ abs ".ld ssen, as well as several piston measuring devices ;;; ^1, are arranged at a distance along the Längener stretching dor cylinder means and operatively connected to the first, second, third and fourth valve means., To cause the piston of the DruckströmungiiKiitteihaminer _f continuously from one end to the other back and forth to move and reaction forces on the cylinder to rotate the cylinder around the first axis. 86. Execution of claim 85, characterized labeled in 2 "ICHR; 2t _f that the diametrically opposite Eridvvände the S-shaped pressure fluid chamber in each case in a substantially radial plane loading ■ zügiich the axis of rotation are arranged. 87. Device according to claim 85, characterized in that two piston measuring devices each are located near the outer ends of the S-shaped fluid chamber and each from the first and second valve device, which open the adjacent one when the piston approaches the associated outer end dex ~ S-shaped pressurized fluid chamber approaches. BAD ORIGINAL ORIGINAL INSPECTED 88. Device according to claim 85, characterized in that two of the two piston measuring devices are each arranged near the outer ends of the S-shaped pressure flow siaifctelkammer and each. are effective to the first and second Ventileinric 'ti'iig the closest, and by the third and vier.t;?. angeordrieta -an the valve means with open Diametralabfitand zn / when the piston the zugehör.iCjer. Ar.venende of the S-shaped pressure opacifier.T.'Tiej: :: - Sr en that a third and fourth piston measuring direction is arranged accordingly along the middle section of the 3 ~: r ^v jrraigen pressure fluid chamber . and that the third piston measuring device on the J-Cc.uuevL-tfwecrang in one direction and the fourth KoI-berii.vaj ?. . ^ inri; caution responds to the piston movement in the opposite direction, uia to close the open one of the first and second valve, u: ü to allow the £ ;; <pc-.nsion of the compressed gas driving the piston. 89. Device according to claim 65, 74, 76, 77, 79 or c5.f characterized in that the S-shaped Longitudinal axis of the pressure fluid chamber the first Axis intersects.
25th 90. Mechanism of extraction of mechanical energy cius compressed gas, characterized by the following steps: 1.) Erection of a cylinder that has an S-shaped print
^ou forms fluid chamber around an axis which is transverse to the longitudinal axis of the cylinder at its center, 2.) Insertion of a free piston element into the S-shaped pressure fluid chamber for sliding and sealing movement herein, 3.) applying a valve head to each end of the cylinder: each valve head having a power-operated intake and exhaust valve, and 4.) Open dos inlet valves to pressurized fluid admit, and close the exhaust valve at one end of the cylinder and close the inlet valve ° tiles and open the outlet valve on the other End of cylinder when the free piston converged approaching an end, with a Wechselbewacruntj of the free piston and a reaction force is generated at the cylinder ends, which supports the rotation. 91, method for expanding and cooling a compressed gas, -.Y ~ 3. while at the same time mechanical energy hiorriUE gt-.v7in.nt, characterized by the following ^lfa very i :. to: 1.) Rotation of a cylinder, which forms an elongated S-shape r
2.) Introduce a free piston element into the central pressure chamber for sealing sliding movement therein, 3.) Fit a valve head at each end of the Zy] .inaers, each valve head being a power operated Has inlet valve and outlet valve, 4.) Open the inlet valve to pressurized fluid let in ^ and close the exhaust valve on a cylinder end and closing, the intake valve and open the exhaust valve on the other cylinder-30 end v; hen the free piston said one end approaches _r wherein a Viechseibewegung of the free piston and a Rekationskraft is generated at the cylinder ends, the rotation thereof untex 'supported, and
35 5.) Closing the open inlet valve in a cylinder after the free piston moves around a has moved the preselected distance to the other end of the cylinder, using a Druckströmgsmlttel- BAD ORIGINAL ORIGINAL INSPECTED -39- * Includes filling and allows it to expand until the free piston comes close to the other end of the cylinder . 92. Process for extracting mechanical energy from eirisa compressed gas, characterized by the following notices - ^. Ü:
1.) Dr ..-. Bo. "Of a cylinder, which forms an S-shaped pressure flow and medium chamber, around an axis which qucl; runs and intersects, with the opposite ends of the S-shaped pressure Rrröaurqsrnittelkami ^ er extending in the direction of rotation of the 2-v:.; - r.di, rs,
2,}: i: = n ae3v. It has a free piston in which S-shaped pressure flow means to carry out a sealing sliding movement, 3.) rna η introduces pressurized gas into the S-shaped pressure s trörriUjigpnittelkammer in order to transmit a kinetic L-iu-rcie to the piston, on the one hand to find the 3-way. igen pressure fluids to move, vf & hieno. the force of the pressurized fluid acts on aa.iT other end of the cylinder to assist the rotation of the cylinder, and 4.) transferring the kinetic energy of the piston to a gas filling in one end of the S-shaped pressurized fluid chamber to further rotate the cylinder to support* ^ow 93. Process for extracting mechanical energy from compressed gas, characterized by the following steps: 1.) Rotating a cylinder that forms an S-shaped pressure fluid chamber forms around an axis that is near the center of the longitudinal axis- 'the S-shaped Pressurized fluid chamber and across it Axis tangles, with the opposite ends of the S-shaped pressurized flow mithelial chamber BADORiGlNAL extend in the direction of rotation of the cylinder, 2.) a free piston is allowed in the S-shaped Druckströmüngsmittelkammer a sealing Carry out sliding movement, 3.) One leads Druckgcis into the S-shaped Druckströrnungsiaittelkcimmer one to impart kinetic energy to the piston in order to move it to one end to move the S-shaped pressurized fluid chamber while the force from the pressurized fluid "-mittel acts on the other end of the cylinder, uie to assist the rotation of the cylinder, and 4.) Tiiari transfers the kinetic energy of the piston on a gas charge in one end of the S-shaped pressurized fluid chamber to stop the To support Svlir-ders even further. ORIGINAL INSPECTED BAD ORIGINAL ^υη