Compressor device and cooling device with compressor device

Abstract

The invention relates to a compressor device (2) comprising a cylinder (4), a piston (6) arranged in the cylinder (4), which piston delimits a transfer chamber (16) filled with a transfer fluid and can be periodically moved back and forth by means of a drive means (26), a compressor element (8), in particular a (metal) bellows, arranged in the transfer chamber (16), the invention relates to a compressor element (10), which defines a working chamber / compression chamber (20) filled with a working gas, and a connection (10), by means of which the working chamber (20) can be connected to a working gas line (36) to form a Gifford-Maxmaflood cooler or a pulse tube cooler (38), the compressor element (8) and the working gas contained therein are indirectly periodically compressed by a transfer fluid discharged by the piston (6).

Description

Technical Field

[0001] The present disclosure relates to a compressor device and a cooling device having a compressor device and a Gifford-McMahon cooler or a pulse tube cooler. Background Art

[0002] Pulse tube coolers or Gifford-McMahon coolers (Gifford-McMahon-Kühler) are widely used to cool magnetic resonance tomographs, cryopumps, quantum computers, quantum communication devices, etc. Here, a gas compressor and in particular a helium compressor is used in combination with a rotary valve or a rotary valve. The helium compressor is connected to the rotary valve via a high-pressure line and a low-pressure line. On the output side, the rotary valve is connected to a cooling device in the form of a Gifford-McMahon cooler or a pulse tube cooler via a gas line. Here, the high-pressure side or the low-pressure side of the gas compressor is alternately connected to the pulse tube cooler or the Gifford-McMahon cooler via a rotary valve. The rate for introducing the compressed helium into the cooling device and implementing it again is in the range of 1-2 Hz. The disadvantage of this cooling system or compressor system is that the motor-driven rotary valve causes a loss of about 50% of the compressor input power.

[0003] A cooling device having a pulse tube cooler or a Gifford-McMahon cooler is known from DE 101 37 552 C1.

[0004] DE633104A discloses a compressor device with a compression mechanism, in which the working medium is periodically compressed and relieved by a reciprocating compressor element in the form of a piston. The drive device comprises a pressure cylinder with a reciprocating piston. Here, the drive device is mechanically coupled to the compressor element. Not only the drive device but also the compressor element is constructed with a separate pressure cylinder, in which a compressor piston or a compressor piston is supported. The drive device and the compressor element are mechanically connected here, wherein the lead-through portion formed by the pressure cylinder is sealed. This structure causes a relatively large space requirement for the equipment because the pressure cylinder is arranged in series. In addition, this structure forces the use of two pistons and two lead-through portions, which are structurally costly and easily fail in terms of sealing. Summary of the invention

[0005] The object of the present invention is to eliminate or at least reduce the disadvantages of the prior art. The object of the present invention is in particular to provide a compressor device and a cooling system which minimizes losses and construction space.

[0006] This object is achieved by a compressor device according to claim 1 and by a cooling device according to the independent claim.

[0007] Specifically, the object is achieved by a compressor device, which has a cylinder, a piston arranged in the cylinder, the piston defining a transfer chamber filled with a transfer fluid and capable of cyclically reciprocating by means of a drive device, a compressor element arranged in the transfer chamber, preferably a bellows, in particular a metal bellows, the compressor element defining a working chamber (compression chamber) filled with a working gas, and a connector, through which the working chamber can be connected to a working gas line (pressure line) to form a Gifford-McMahon cooler or a pulse tube cooler, in particular a two-stage 4K (four Kelvin) cooler, wherein the compressor element and the working gas contained in the compressor element are indirectly compressed / squeezed cyclically by the transfer fluid discharged by the piston.

[0008] In other words, the compressor device includes a cylinder and a piston running in the cylinder, the cylinder having a cylinder running track constructed on the inner side of the cylinder, and the piston having a piston skirt constructed in the circumferential direction of the piston. The piston skirt slides in a sealed manner on the cylinder running track of the cylinder. Preferably, at least one annular seal / piston ring is constructed between the piston skirt and the cylinder running track. The piston also includes a piston top, which faces and defines a transfer chamber filled with a transfer fluid. The piston is arranged and constructed to perform periodic linear motion in the direction of the cylinder centerline extending along the length direction of the cylinder (cylinder center axis). A compressor element is constructed in the transfer chamber, and the compressor element includes at least one preferably accordion-shaped wall. In other words, the compressor element is preferably constructed as a bellows. The compressor element surrounds a working chamber filled with working gas. In other words, the compressor element defines a working chamber relative to the transfer chamber. The working chamber is constructed with a joint, which connects the working chamber to the working gas pipeline fixedly or detachably. The joint is preferably constructed on the side of the compressor element away from the piston. The working gas line is arranged and constructed to connect the working chamber to a Gifford-McMahon cooler or a pulse tube cooler or any other suitable cooler. The volume of the working chamber is variable due to the preferably accordion-shaped wall. By the linear movement of the piston, force is applied / transmitted to the compressor element by means of the transfer fluid, and the working gas contained in the working chamber is cyclically compressed / squeezed and depressurized.

[0009] The core of the invention is therefore to periodically compress and release the working gas contained in the compressor element of the compressor device indirectly by means of a transfer fluid via the displacement of a piston.

[0010] Furthermore, the core of the present invention is to construct pressure generating sites (force generating sites) and compression sites in the cylinder.

[0011] A further core of the invention is that the piston and the compressor element are mechanically decoupled.

[0012] In other words, the piston and the compressor element are arranged in the cylinder so that they never come into contact with each other. In addition, the forces acting on the piston or the forces to be transmitted by the piston are only transmitted hydraulically to the compressor element. In the present invention, a mechanical connection for force transmission is omitted between the piston and the compressor element.

[0013] By configuring the compressor device in this way, it is possible to dispense with a rotary valve and thus reduce losses and thus significantly increase the efficiency of the compressor device. In addition, since a single-cylinder design of the compressor device can be achieved, such a compressor device can be designed more compactly. A further advantage of such a compressor device is that the failure safety of the compressor device can be increased by reducing the number of components.

[0014] By configuring the working chamber in the compressor element, in particular by configuring the compressor element as a metal bellows, it is also possible to prevent water, transfer fluid, oil or other impurities from entering / diffusing into the working gas and contaminating / contaminating the working gas. Contamination of the working gas by impurities can lead to freezing of the working gas and damage to the seal. In particular, configuring the compressor element as a metal bellows has the advantage over configuring the compressor element from rubber, for example, that the working gas cannot leak out of the compressor element or through the compressor element into the transfer chamber.

[0015] In a first aspect, the volume of the space / fluid chamber enclosed by the piston, the compressor element and the cylinder may be constant.

[0016] In other words, the region of the transfer chamber outside the compressor element / working room may be completely filled with the transfer fluid, wherein the transfer fluid may be a substantially incompressible fluid.

[0017] In this way, it can be ensured that the force exerted by the piston on the transfer fluid can be transmitted to the bellows uniformly and without local force peaks. This ensures that the compressor element is compressed and expanded only in the intended manner, which significantly prolongs the service life of the compressor element and prevents premature failure of the compressor element. In addition, by completely filling the transfer chamber with the transfer fluid, foaming or foam formation of the transfer fluid during operation can be prevented.

[0018] Furthermore, the transfer chamber and the working chamber can be formed completely in the cylinder and without projections.

[0019] On the other hand, the pressure of the working medium in the working chamber can correspond to the pressure of the transfer fluid in the transfer chamber at any point in time.

[0020] In other words, at any point in time, the pressure in the compressor element corresponds to the pressure surrounding the compressor element. In yet other words, the working medium in the working chamber and the transfer fluid in the transfer chamber are in pressure equilibrium.

[0021] In this way it can be ensured that the compressor element itself is not subjected to or does not absorb high loads / forces and that the compressor element can be designed with thin walls, which further reduces losses during compression of the compressor element.

[0022] On the other hand, the pressure of the working medium and the pressure of the transfer fluid may be greater than the ambient pressure of the environment surrounding the compressor device.

[0023] In other words, the compressor arrangement is preloaded so that in every position of the piston in the cylinder there is an overpressure of the working medium and the transfer medium relative to the surroundings.

[0024] In another aspect, the maximum piston stroke may be greater than the maximum compressor element stroke.

[0025] In other words, the amplitude implemented by the piston during the periodic reciprocating movement in the piston movement direction can be greater than the maximum change of the compressor element extension of the compressor element in the piston movement direction.

[0026] The result of a smaller maximum compressor element stroke is that the mechanical loads on the compressor element, in particular during bending / folding of the compressor element, are kept low, which prolongs the service life of the compressor element and reduces the risk of failure.

[0027] On the other hand, the piston can be reciprocated periodically by a connecting rod. Through the connecting rod used to move the piston, a conventional electric motor can be used as a drive device. Alternatively, the piston can be reciprocated by a threaded rod or the like.

[0028] On the other hand, the compressor element can be guided in the stroke direction.

[0029] In other words, the compressor device can include at least one guide element, which is configured to guide the compression element during compression and decompression and prevent the compressor element from bending or collapsing uncontrollably. The guide element can be configured, for example, in the form of a rod or sleeve. Preferably, more than one guide element can be configured in the compressor device.

[0030] On the other hand, a closed displacer (pot element) can be formed in the working chamber.

[0031] In other words, a displacement element can be formed on the inner side of the compressor element facing the working chamber, preferably on the end side of the compressor element close to the piston. The displacement element can be an element which is closed in a gas-tight manner per se, in particular a cylindrical element which can be designed to be fixedly connected to the compressor element.

[0032] The (gas) volume of the working chamber can be reduced by such a displacement element in the working chamber. It can thus be achieved that the working chamber has an approximately zero (dead / residual) volume in the compressed state, which reduces the deflection of the compressor element and thus reduces the load on the compressor element.

[0033] On the other hand, the maximum longitudinal extension of the compressor element in the stroke direction in the expanded state may be twice the minimum longitudinal extension of the compressor element in the stroke direction in the compressed state.

[0034] On the other hand, the transfer chamber and / or the working chamber can be connected to at least one balancing container, optionally via a valve, in order to preload the compressor device and to compensate for possible volume changes, in particular during acceleration or start-up of the compressor device.

[0035] On the other hand, the compression of the compressor element is reversible. This means that the volume of the compressor element changes only within a predefined range during operation and then returns to the original geometry.

[0036] In another aspect, the wall thickness of the compressor element may be constant.Preferably, the wall thickness of the compressor element may be less than 0.2 mm.

[0037] On the other hand, the compressor element can be constructed from a plurality of membrane pairs. Preferably, the compressor element can be constructed from at least 30 membrane pairs. Particularly preferably, the compressor element can be constructed from at least 40 membrane pairs.

[0038] By configuring the compressor element with a plurality of membrane pairs, it can be ensured that each of the membrane pairs undergoes only a small deflection during the stroke movement of the compressor element, which significantly reduces the mechanical load on the compressor element.

[0039] On the other hand, the transfer chamber can be designed with a multi-stage geometry, in particular a two-stage geometry. In other words, the transfer chamber can have a diameter change, wherein a first diameter in the region of the piston can preferably be smaller than a second diameter in the region of the compressor element. In this way, the force to be applied by the piston for displacing the transfer fluid can be adapted to the drive force or drive torque of the drive device.

[0040] On the other hand, the drive means can be designed with and / or connected to a control means which controls the compression / extrusion and the relief of the working medium in the working chamber via a periodic longitudinal movement of the piston, in particular via a rotational speed of the drive means.

[0041] On the other hand, the displacement volume displaced by the piston during its movement can vary in accordance with the working chamber volume, thereby significantly simplifying the control of the compressor device.

[0042] In another aspect, a filter may be connected downstream of the compressor device.

[0043] In another aspect, the working medium may be helium.

[0044] Advantageously, the movement profile of the piston is not a linear or sinusoidal profile, but follows a step function, wherein the working gas is rapidly compressed, the pressure is maintained and then the working gas is rapidly relieved again. This movement profile can be achieved by corresponding variable control of the drive means.

[0045] Alternatively, the drive means can be controlled in the same manner and the step-function movement of the piston can be achieved by means of a corresponding transmission element, such as a cam. In other words, the linear movement of the drive means can be converted into an almost step-function movement of the piston by means of a cam-shaped transmission element. In other words, the transmission element can be asymmetrical about the axis of rotation of the transmission element.

[0046] On the other hand, the drive device can drive more than one compressor device. In this configuration, the cylinders can preferably be arranged in an opposing formation (boxer formation). In other words, for example, two cylinders can be constructed by the drive device diametrically opposed, wherein the cylinders can be constructed identically. Each cylinder can be constructed with a piston and a compressor element.

[0047] In another aspect, the transmission fluid can (also) be used as a lubricant for the drive means. In other words, on the side of the piston facing away from the transmission chamber, the transmission fluid can be configured as a lubricant. In particular, the transmission fluid can lubricate the motor connecting rod pair and the connecting rod piston pair. By configuring the transmission fluid as a lubricant, it is possible to prevent the transmission fluid from leaking through the piston towards the drive means and having a negative impact on the drive means.

[0048] On the other hand, the compressor device can be designed for an operating frequency range between 0.1 Hz and 10 Hz and in particular for an operating frequency range between 0.5 Hz and 5 Hz.

[0049] Furthermore, the object is achieved by a cooling device having a compressor device according to any of the above aspects and a Gifford-McMahon cooler or a pulse tube cooler.

[0050] In other words, the cooling device includes a compressor device according to any one of the above aspects and a Gifford-McMahon cooler or a pulse tube cooler connected via a joint. Optionally, a heat exchanger for cooling the working gas may be constructed between the cooling device and the Gifford-McMahon cooler or the pulse tube cooler, or the cooling device may be directly constructed on the Gifford-McMahon cooler or the pulse tube cooler.

[0051] In this way, the rotary valve can be omitted and the pressure curve can be established directly using the compressor device. The Gifford-McMahon cooler or pulse tube cooler can be connected directly to the compressor device. For the operation of the Gifford-McMahon cooler or pulse tube cooler, extremely pure helium (6N=99.9999% helium) is required.

[0052] In one aspect, the compressor assembly and the Gifford-McMahon cooler or pulse tube cooler may be connected via a high pressure connection.

[0053] On the other hand, the cooling device or the compressor device may be preloaded at 16 bar. The operating range of the compressor device may be between 8 bar and 24 bar.

[0054] Furthermore, a compressor refrigerator may be configured with the compressor device according to any one of the above aspects, an evaporator and a condenser. BRIEF DESCRIPTION OF THE DRAWINGS

[0055] Figure 1 is a schematic diagram of a compressor arrangement according to the invention in a general embodiment;

[0056] Figure 2 is a schematic diagram of a compressor arrangement according to the invention in a particular embodiment;

[0057] Figure 3 is a schematic diagram of the structure of a cooling device according to the present invention in a first embodiment;

[0058] Figure 4 is a schematic diagram of the structure of a cooling device according to the present invention in a second embodiment;

[0059] Figure 5 is a schematic diagram of a compressor arrangement according to the invention in a first alternative embodiment;

[0060] Figure 6 is a schematic diagram of a compressor arrangement according to the invention in a second alternative embodiment;

[0061] Figure 7 is a schematic diagram of a compressor arrangement according to the invention in a third alternative embodiment; and

[0062] Figure 8 is a schematic diagram of a compressor arrangement according to the invention in a fourth alternative embodiment. DETAILED DESCRIPTION

[0063] Embodiments of the present disclosure are described below based on the drawings.

[0064] Figure 1A compressor device 2 according to the invention is shown, having a gas-tight cylinder 4, a piston 6 arranged in the cylinder 4, a compressor element in the form of a (metal) bellows 8 and a connection 10, wherein the compressor device 2 is arranged and configured to be coupled to a cooling device or to form part of a cooling device. The cylinder 4 comprises a (cylinder) working surface 12 configured on the inner side of the cylinder 4. The piston 6 comprises a piston skirt 14 configured on the outer peripheral surface of the piston 6, wherein the working surface 12 of the cylinder 4 and the piston skirt 14 of the piston 6 are coordinated with each other so that the piston 6 can move linearly in the cylinder 4 along the cylinder center axis ZM in a sealed manner. The piston 6 and the cylinder 4 define a transfer chamber 16. The transfer chamber 16 is filled with a transfer fluid. The bellows 8 is arranged in the transfer chamber 16 and is surrounded by the (incompressible) transfer fluid. Specifically, the transfer fluid is configured in a fluid chamber 18 surrounded / enclosed between the cylinder 4, the piston 6 and the bellows 8. The volume of the fluid chamber 18 is essentially invariable, wherein, however, the geometry of the fluid chamber 18 can be varied.

[0065] The bellows 8 contains / delimits a working chamber 20. The working chamber 20 is filled with a working gas, preferably helium. In the embodiment shown here, the bellows 8 is designed as a bellows with an accordion-shaped wall 22. The bellows 8 separates the transfer chamber 16 and the working chamber 20 from each other in an airtight and fluid-tight manner. The connection 10 is formed on the side of the working chamber 20 facing away from the piston 6. The connection 10 is arranged and configured to connect the compressor device 2 to a cold head / cooler 38 (see Figure 3 ), such as a Gifford-McMahon cooler or a pulse tube cooler connection.

[0066] Figure 2 The compressor device 2 is shown in an embodiment in which the piston 6 is linearly movable along the cylinder center axis ZM by means of a connecting rod 24 .

[0067] Below with the help of Figure 2 The operation of the compressor device 2 according to the present invention is described. The driving of the piston 6 by the connecting rod 24 is exemplary. Of course, other driving methods of the piston 6 that can make the piston 6 reciprocate periodically along the cylinder center axis ZM are considered equivalent.

[0068] A drive device in the form of an electric motor 26, which is controlled by a corresponding control device (not shown), drives the disk 28 in rotation, on which the connecting rod 24 is eccentrically supported at a first bearing point 30. In addition, the connecting rod 24 is supported / fixed on the piston 6 at a second bearing point 32. The linear movement of the piston 6 along the cylinder center axis ZM is generated by the rotary / circular movement of the disk 28 via the connecting rod 24. In other words, the force generated by the electric motor 26 is transmitted to the piston 6 via the disk 28 and the connecting rod 24.

[0069] When the piston 6 moves along the cylinder center axis ZM in the direction of the bellows 8 side, the force is transmitted to the transmission fluid in the fluid chamber 18. The transmission fluid surrounding the bellows 8 transmits the force to the bellows 8 and compresses the working gas contained in the bellows 8. Since the transmission fluid is a nearly incompressible fluid, the force applied by the electric motor 26 (minus possible friction losses) is basically completely converted into the compression of the bellows 8 and the compression of the working gas in the working chamber 20. In other words, the working gas in the working chamber 20 is periodically compressed by the force of the electric motor 26. Here, the working range of the bellows 8 is between the first length L1 in the compressed state and the second length L2 in the decompressed state. The (maximum) length change ΔL of the bellows 8 is much smaller than the first length L1 or the second length L2, and the length change corresponds to the difference between the first length L1 and the second length L2.

[0070] Figure 3 A cooling device 34 according to the invention is shown with a compressor device 2 in a first embodiment. The working chamber 20 of the compressor device 2 is connected to a pressure line 36 via a connection 10. The pressure line 36 connects the compressor device 2 in a gas-tight manner to a cold head 38 designed as a Gifford-McMahon cooler or a pulse tube cooler. To operate such a cold head 38, a defined working gas volume is cyclically compressed and depressurized by the compressor device 2 in a predetermined frequency range.

[0071] Figure 4 A cooling device 34 according to the invention is shown with a compressor device 2 in a second embodiment. The cooling device 34 of the second embodiment corresponds substantially to the cooling device 34 of the first embodiment. In the second embodiment, a heat exchanger 40 is formed between the connection 10 and the cold head 38 of the compressor device 2, which is provided and designed to cool down the working gas, in particular after compression.

[0072] According to the following Figures 5 to 8 An alternative embodiment of the compressor device 2 is described. Figure 1 The corresponding elements of the general embodiment described in the accompanying drawings are described again.

[0073] exist Figure 5 The first alternative embodiment of the compressor device 2 shown in FIG. 4 includes a tank element 42 in the bellows 8. The tank element 42 is formed on the end side of the bellows 8 facing the piston 6 in the working room 20. The tank element 42 reduces the gas volume / internal volume of the working room 20. The tank element 42 is gas-tightly closed relative to the working room 20.

[0074] Figure 6A second alternative embodiment of a compressor device 2 is shown with an axle-shaped or rod-shaped guide element 44. The rod-shaped guide element 44 is formed in the transfer chamber 16 on the end side of the bellows 8 facing the piston 6. The rod-shaped guide element 44 extends away from the bellows 8 toward the piston 6 and is supported in the piston 6. The rod-shaped guide element 44 is linearly guided or supported in the piston 6. Preferably, the rod-shaped guide element 44 is guided or supported in a bushing in the piston 6. Optionally, more than one rod-shaped guide element 44 is formed on the bellows 8. The rod-shaped guide element 44 prevents the bellows 8 from tilting relative to the piston 6.

[0075] Figure 7 A third alternative embodiment of a compressor device 2 is shown with a flat guide element 46. The flat guide element 46 is formed in the transfer chamber 16 on the end side of the bellows 8 facing the piston 6. The flat guide element 46 extends radially outwards toward the working surface 12 and guides the bellows 8 relative to the working surface 12. A hole 48 is formed in the flat guide element 46, which ensures an unimpeded flow of the transfer fluid in the transfer chamber. The flat guide element 46 prevents the bellows 8 from tilting relative to the cylinder 4.

[0076] Figure 8 A fourth alternative embodiment of a compressor device 2 is shown, in which the cylinder 4 is designed in two stages. The cylinder 4 comprises a first cylinder section 50, in which the bellows 8 is formed, and a second cylinder section 52, in which the piston 6 is formed. The first diameter of the first cylinder section 50 is greater than the second diameter of the second cylinder section 52. In other words, a pressure conversion in the cylinder 4 is achieved by the first cylinder section 50 and the second cylinder section 52.

[0077] Of course, the features of all described embodiments may be combined arbitrarily in the claims, if technically feasible.

[0078] It is thus conceivable, for example, to construct the compression device 2 with a pot element 42 in the working chamber 20 and to additionally construct the bellows 8 with a rod-shaped guide element 44 and / or a flat guide element 46 .

[0079] It is also conceivable that the compression device 2 is designed with a cylinder 4 having a first cylinder section 50 and a second cylinder section 52 and a cup element 42 .

[0080] Furthermore, it is conceivable that the compressor device is designed with a cylinder 4 having a first cylinder section 50 and a second cylinder section 52 , a cup element 42 and a rod-shaped guide element 44 and / or a flat guide element 46 .

[0081] Reference numerals list

[0082] 2Compressor unit

[0083] 4 cylinders

[0084] 6 Piston

[0085] 8 Bellows

[0086] 10 connectors

[0087] 12 (cylinder) working surface

[0088] 14 Piston skirt

[0089] 16 Transfer Room

[0090] 18 Fluid Chamber

[0091] 20 Studio

[0092] 22 wall

[0093] 24 Connecting rod

[0094] 26 Electric Motor

[0095] 28 plates

[0096] 30 First support position

[0097] 32 Second support position

[0098] 34 Cooling device

[0099] 36 Pressure line

[0100] 38 Cold Head

[0101] 40 Heat exchanger

[0102] 42 tank components / exhaust components

[0103] 44 Rod-shaped guide element

[0104] 46 Flat guide element

[0105] 48 holes

[0106] 50 First cylinder section

[0107] 52 Second cylinder section

[0108] ZM cylinder center axis

[0109] L1 First length

[0110] L2 Second length

[0111] ΔL Length change

Claims

1. A compressor device (2) having Cylinder (4), a piston (6) arranged in the cylinder (4), the piston defining a transfer chamber (16) filled with a transfer fluid and capable of periodic reciprocating motion by means of a drive means (26); a compressor element (8), in particular a (metal) bellows, arranged in the transfer chamber (16), which defines a working chamber (20) filled with a working gas, and A connector (10), through which the working chamber (20) can be connected to a working gas pipeline (36) to form a Gifford-McMahon cooler or a pulse tube cooler (38); in, The compressor element (8) and the working gas contained therein are cyclically compressed indirectly by means of a transfer fluid expelled by the piston (6).

2. The compressor device (2) according to claim 1, wherein: The volume of the (fluid) space (18) enclosed by the piston (6), the compressor element (8) and the cylinder (4) is constant.

3. The compressor device (2) according to any one of claims 1 or 2, wherein: The transfer chamber (16) and the working chamber (20) are completely formed in the cylinder (4).

4. The compressor device (2) according to any one of claims 1 to 3, wherein: The pressure of the working medium in the working chamber (20) corresponds at any point in time to the pressure of the transfer fluid in the transfer chamber (16).

5. The compressor device (2) according to claim 4, wherein: The pressure of the working medium and the pressure of the transfer fluid are greater than the ambient pressure of the environment surrounding the compressor device (2).

6. The compressor device (2) according to any one of claims 1 to 5, wherein: The maximum piston stroke is greater than the maximum compressor element stroke (ΔL).

7. The compressor device (2) according to any one of claims 1 to 6, wherein: The piston (6) can periodically reciprocate via a connecting rod (24).

8. The compressor device (2) according to any one of claims 1 to 7, wherein: The compressor element (8) is guided in the stroke direction.

9. The compressor device (2) according to any one of claims 1 to 8, wherein: A closed displacement element (42) is formed in the working chamber (20).

10. A cooling device (34) having a compressor device (2) according to any one of claims 1 to 9 and a Gifford-McMahon cooler or a pulse tube cooler (38).

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