CN117605686A - Fluid machine and heat exchange device - Google Patents

Abstract

The invention provides a fluid machine and heat exchange equipment, wherein the fluid machine comprises a crankshaft, a cylinder sleeve, a cross groove structure, a sliding block, an upper flange and a lower flange, wherein the crankshaft is axially provided with a first eccentric part and a second eccentric part; the crankshaft and the cylinder sleeve are eccentrically arranged; the cross groove structure is rotatably arranged in the cylinder sleeve, a first limiting channel and a second limiting channel of the cross groove structure are sequentially arranged along the axial direction of the crankshaft, the extending direction of the first limiting channel and the extending direction of the second limiting channel are perpendicular to the axial direction of the crankshaft, and the second eccentric part is slidably arranged in the second limiting channel and forms a limiting cavity; the first eccentric part extends into the through hole of the sliding block, and the sliding block is arranged in the first limiting channel in a sliding manner and forms a variable-volume cavity; the upper flange and the lower flange are respectively arranged at two axial ends of the cylinder sleeve, the end face of the lower flange facing one side of the cylinder sleeve is provided with a pressure relief ring groove, and the pressure relief ring groove is used for communicating the two limiting cavities. The invention solves the problems of low energy efficiency and larger power consumption of the compressor in the prior art.

Description

Fluid machine and heat exchange device

Technical Field

The invention relates to the technical field of heat exchange systems, in particular to a fluid machine and heat exchange equipment.

Background

The fluid machinery in the prior art includes compressors, expanders, and the like. Taking a compressor as an example.

According to national energy-saving and environment-friendly policies and consumer requirements for air conditioning comfort, the air conditioning industry is always pursuing high efficiency and low noise. The compressor acts as the heart of the air conditioner, having a direct impact on the energy efficiency and noise level of the air conditioner. The rolling rotor type compressor is used as a main stream of household air conditioner compressors, has been developed for nearly one hundred years, is relatively mature, is limited by a structural principle, and has limited optimization space. In order to make a major breakthrough, innovation is required from the structural principle.

Therefore, it is highly desirable to provide a compressor having the characteristics of high energy efficiency, low noise, and the like.

Disclosure of Invention

The invention mainly aims to provide a fluid machine and heat exchange equipment so as to solve the problems of low energy efficiency and high power consumption of a compressor in the prior art.

In order to achieve the above object, according to one aspect of the present invention, there is provided a fluid machine including a crankshaft, a cylinder liner, a cross groove structure, a slider, an upper flange, and a lower flange, wherein the crankshaft is provided with a first eccentric portion and a second eccentric portion in an axial direction thereof; the crankshaft and the cylinder sleeve are eccentrically arranged, and the eccentric distance is fixed; the cross groove structure is rotatably arranged in the cylinder sleeve and is provided with a first limiting channel and a second limiting channel, the first limiting channel and the second limiting channel are sequentially arranged along the axial direction of the crankshaft, the first limiting channel is positioned above the second limiting channel, the extending direction of the first limiting channel and the second limiting channel is perpendicular to the axial direction of the crankshaft, the second eccentric part is slidably arranged in the second limiting channel and forms a limiting cavity, and the limiting cavity is positioned in the sliding direction of the second eccentric part; the sliding block is provided with a through hole, the first eccentric part extends into the through hole, the sliding block is arranged in the first limiting channel in a sliding way to form a variable-volume cavity, the variable-volume cavity is positioned in the sliding direction of the sliding block, and the crankshaft rotates to drive the sliding block to slide back and forth in the first limiting channel and interact with the cross groove structure so as to enable the cross groove structure and the sliding block to rotate in the cylinder sleeve; the upper flange and the lower flange are respectively arranged at two axial ends of the cylinder sleeve, the upper flange and the lower flange are respectively provided with an avoidance via hole for avoiding a crankshaft, the end face of the lower flange, which faces one side of the cylinder sleeve, is provided with a pressure relief ring groove, the pressure relief ring groove is positioned at the peripheral side of the avoidance via hole, and the pressure relief ring groove is used for communicating the two limiting cavities.

Further, the avoidance through hole and the lower flange are concentrically arranged, and the pressure relief ring groove and the lower flange are eccentrically arranged.

Further, the height of the first eccentric portion in the axial direction of the crankshaft is greater than the height of the second eccentric portion in the axial direction of the crankshaft.

Further, the second limiting channel directly penetrates through the end face of the cross groove structure along the axial direction of the cross groove structure, so that one end of the cross groove structure is in an open shape, an opening for a crankshaft to extend out is reserved on the end face of one end of the cross groove structure, which is not in the open shape, and the opening is concentrically arranged with the cross groove structure and communicated with the first limiting channel.

Further, the inner diameter D1 of the pressure relief ring groove, the outer diameter D2 of the pressure relief ring groove and the diameter D5 of the shaft body part of the crankshaft positioned on one side of the second eccentric part far away from the first eccentric part satisfy the following conditions: D1-D5 is less than or equal to 1mm and less than or equal to D2.

Further, the cross groove structure is provided with a central hole, the central hole is used for communicating the first limiting channel and the second limiting channel, and the outer circle diameter D2 of the pressure relief ring groove, the hole diameter D3 of the central hole and the outer circle diameter D4 of the cross groove structure meet the following conditions: D4-D2 is more than or equal to 0.1mm and less than or equal to D3.

Further, the groove section of the pressure relief ring groove is one of round, square and oval.

Further, at least one oil drain hole is formed in the bottom surface of the pressure relief ring groove, and the oil drain hole penetrates through the end surface of one side, far away from the cylinder sleeve, of the lower flange, so that the oil drain hole is communicated with the outside.

Further, the oil drain hole is formed at the bottom surface of the groove at the distal end side of the pressure relief ring groove.

Further, a phase difference of a first included angle A is formed between the first eccentric part and the second eccentric part, the eccentric amount of the first eccentric part is equal to that of the second eccentric part, and a phase difference of a second included angle B is formed between the extending direction of the first limiting channel and the extending direction of the second limiting channel, wherein the first included angle A is twice the second included angle B.

Further, the first eccentric portion and the second eccentric portion are disposed 180 ° opposite to each other.

According to another aspect of the present invention, there is provided a heat exchange apparatus comprising a fluid machine, the fluid machine being the fluid machine described above.

By adopting the technical scheme, the cross groove structure is arranged to be in a structure form with the first limiting channel and the second limiting channel, meanwhile, the second eccentric part is arranged in the second limiting channel in a sliding way to form the limiting cavity, the limiting cavity is positioned in the sliding direction of the second eccentric part, in addition, the sliding block is arranged in the first limiting channel in a sliding way to form the variable-volume cavity, the variable-volume cavity is positioned in the sliding direction of the sliding block, and the crankshaft rotates to drive the sliding block to reciprocally slide in the first limiting channel and interact with the cross groove structure, so that the cross groove structure and the sliding block rotate in the cylinder sleeve, the dead point position of the fluid machine is avoided, the movement reliability of the fluid machine is improved, and the working reliability of the heat exchange equipment is ensured.

It should be noted that, through seting up the pressure release annular on the terminal surface of lower flange towards cylinder liner one side for pressure release annular communicates two spacing chambeies, like this, is convenient for in time discharge the frozen oil, thereby ensures the rotation reliability of bent axle, has avoided increasing the consumption of fluid machinery.

Further, since the fluid machine provided by the application can stably operate, that is, the energy efficiency of the compressor is ensured to be high, so that the working reliability of the heat exchange equipment is ensured.

Drawings

The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention. In the drawings:

FIG. 1 shows a schematic structural view of a pump body assembly of a compressor according to an alternative embodiment of the present invention;

FIG. 2 shows a schematic cross-sectional structural view of the view C-C of FIG. 1;

FIG. 3 shows an exploded view of the pump body assembly of FIG. 1;

FIG. 4 shows a schematic view of the lower flange of the pump body assembly of FIG. 1;

FIG. 5 shows a schematic structural view of a crankshaft of the pump body assembly of FIG. 3;

FIG. 6 shows a schematic cross-sectional structural view of the cross-slot configuration of the pump body assembly of FIG. 3;

FIG. 7 is a schematic cross-sectional view of the pump body assembly of FIG. 1, showing a schematic cross-slot configuration rotated 0 by the crankshaft;

FIG. 8 is a schematic view showing a state of the cross groove structure rotated 90 DEG by the crankshaft in FIG. 7;

FIG. 9 is a schematic view showing a state of the cross groove structure rotated 180 DEG by the crankshaft of FIG. 8;

FIG. 10 is a schematic view showing a state of the cross groove structure rotated 270 DEG by the crankshaft of FIG. 9;

FIG. 11 shows a schematic structural view of a lower flange of a pump body assembly according to another alternative embodiment of the present invention;

fig. 12 shows a schematic structural view of a crankshaft of the pump body assembly of fig. 3.

Wherein the above figures include the following reference numerals:

10. a crankshaft; 11. a first eccentric portion; 12. a second eccentric portion; 121. a eccentric portion sink; 13. sinking grooves of the crankshaft;

20. cylinder sleeve;

30. a cross slot structure; 31. a first limiting channel; 32. the second limiting channel; 321. a spacing cavity; 33. opening holes; 34. a central bore;

40. a slide block; 41. a through hole; 50. an upper flange;

60. a lower flange; 61. a pressure relief ring groove; 611. an oil drain hole;

100. avoiding the via hole.

Detailed Description

The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.

It should be noted that, the two cylinders of the compressor with double-cylinder rotary cylinder pistons are symmetrically arranged at 180 degrees, so that the change of the load torque can be flattened, therefore, the vibration of the compressor is very small, but the leakage loss of the gas of the compressor is very high due to the defect of the compressor; the gas leakage loss of the compressor of the single-cylinder rotary cylinder piston is small, but the torque peak value is large, the vibration quantity of the compressor is also large, and when the pump body of the single-cylinder rotary cylinder compressor rotates to a certain specific angle, the torque is zero, so that the compressor cannot be started under the rotation angle.

In order to solve the above problems, the second limiting channel 32 of the double-cylinder compressor can be reduced in size, and is changed into a torque balancing device to be used without participating in the air suction and exhaust of the compressor, so that a new structural form is created, hereinafter referred to as a single-cylinder limiting device, and a large number of experiments show that the single-cylinder limiting device inherits the advantages of double cylinders and single cylinders at the same time, and the advantages of the rotary cylinder compressor are further expanded; meanwhile, there are some corresponding problems that when the compressor is operated, the refrigerating oil in the oil pool is conveyed between each friction pair in the pump body assembly through the central oil hole on the crankshaft 10, and the refrigerating oil in the cross groove structure 30 cannot be timely discharged because the second limiting channel 32 does not participate in air suction and air discharge, and at this time, the refrigerating oil in the cross groove structure 30 can obstruct the rotation of the crankshaft 10, so that the power consumption of the compressor is increased.

In order to solve the problems of low energy efficiency and high power consumption of the compressor in the prior art, the invention provides a fluid machine and heat exchange equipment, wherein the heat exchange equipment comprises the fluid machine, and the fluid machine is the fluid machine.

As shown in fig. 1 to 12, the fluid machine includes a crankshaft 10, a cylinder liner 20, a cross groove structure 30, a slider 40, an upper flange 50, and a lower flange 60, wherein the crankshaft 10 is provided with a first eccentric portion 11 and a second eccentric portion 12 in the axial direction thereof; the crankshaft 10 and the cylinder sleeve 20 are eccentrically arranged and the eccentricity is fixed; the cross groove structure 30 is rotatably arranged in the cylinder sleeve 20, the cross groove structure 30 is provided with a first limiting channel 31 and a second limiting channel 32, the first limiting channel 31 and the second limiting channel 32 are sequentially arranged along the axial direction of the crankshaft 10, the first limiting channel 31 is positioned above the second limiting channel 32, the extending direction of the first limiting channel 31 and the second limiting channel 32 is perpendicular to the axial direction of the crankshaft 10, the second eccentric part 12 is slidably arranged in the second limiting channel 32 and forms a limiting cavity 321, and the limiting cavity 321 is positioned in the sliding direction of the second eccentric part 12; the sliding block 40 is provided with a through hole 41, the first eccentric part 11 stretches into the through hole 41, the sliding block 40 is arranged in the first limiting channel 31 in a sliding mode to form a variable volume cavity, the variable volume cavity is positioned in the sliding direction of the sliding block 40, the crankshaft 10 rotates to drive the sliding block 40 to slide back and forth in the first limiting channel 31 and interact with the cross groove structure 30, so that the cross groove structure 30 and the sliding block 40 rotate in the cylinder sleeve 20; the upper flange 50 and the lower flange 60 are respectively arranged at two axial ends of the cylinder sleeve 20, the upper flange 50 and the lower flange 60 are respectively provided with a through hole 100 for avoiding the crankshaft 10, the end face of the lower flange 60, which faces one side of the cylinder sleeve 20, is provided with a pressure relief ring groove 61, the pressure relief ring groove 61 is positioned at the outer peripheral side of the through hole 100, and the pressure relief ring groove 61 is used for communicating the two limiting cavities 321.

By arranging the cross groove structure 30 in a structure form with the first limiting channel 31 and the second limiting channel 32, meanwhile, the second eccentric part 12 is slidably arranged in the second limiting channel 32 and forms a limiting cavity 321, the limiting cavity 321 is positioned in the sliding direction of the second eccentric part 12, in addition, the sliding block 40 is slidably arranged in the first limiting channel 31 and forms a variable-volume cavity, the variable-volume cavity is positioned in the sliding direction of the sliding block 40, and the crankshaft 10 rotates to drive the sliding block 40 to reciprocally slide in the first limiting channel 31 and interact with the cross groove structure 30 so as to enable the cross groove structure 30 and the sliding block 40 to rotate in the cylinder sleeve 20, thus, the dead point position of a fluid machine is avoided, the movement reliability of the fluid machine is improved, and the working reliability of the heat exchange equipment is ensured.

It should be noted that, by opening the pressure relief ring groove 61 on the end surface of the lower flange 60 facing the cylinder sleeve 20, the pressure relief ring groove 61 is communicated with the two limiting cavities 321, so that the frozen oil is conveniently discharged in time, thereby ensuring the rotation reliability of the crankshaft 10 and avoiding the increase of the power consumption of the fluid machinery.

Further, since the fluid machine provided by the application can stably operate, that is, the energy efficiency of the compressor is ensured to be high, so that the working reliability of the heat exchange equipment is ensured.

In this application, as shown in fig. 1, 2, and 7 to 10, unlike the rotor compressor, the compressor of this application is designed such that there is an eccentric between the cylinder liner 20 and the crankshaft 10, and when the compressor is operated, the crankshaft 10 drives the sliding block 40 and the cross groove structure 30 to rotate in the cylinder liner 20, the cross groove structure 30 and the crankshaft 10 rotate around their respective centers, and the sliding block 40 reciprocates simultaneously with respect to the cross groove structure 30 and the crankshaft 10. The reciprocating motion of the slide block 40 relative to the cross slot structure 30 achieves periodic enlargement and reduction of the variable volume cavity; the crossed groove structure 30 moves circularly relative to the cylinder sleeve 20, so that the variable volume cavity is communicated with the air suction channel and the air discharge channel respectively; the two compound motions realize the suction, compression and exhaust processes of the compressor. The second limiting channel 32 and the second eccentric portion 12 cooperate to form a limiting cavity 321, which also has a periodically enlarged and reduced cavity, but the limiting cavity 321 has no matched air intake and exhaust channel, so as not to participate in compression.

The inside of the compressor is usually filled with a certain amount of refrigerating oil for cooling and lubricating the pump body assembly, and the refrigerating oil level generally flows over the cylinder sleeve 20, and the central oil hole of the crankshaft 10 is used for continuously supplying oil between the friction pairs of the pump body assembly, so that the limit cavity 321 is always full of oil. The oil is incompressible, and the gap between the friction pairs is small, so that the oil is difficult to transfer. The rotation resistance of the second eccentric portion 12 increases, thereby increasing the power consumption of the compressor, and thus providing a solution for connecting the two limiting chambers 321.

It should be noted that, in the present application, the fluid machine includes a compressor, which is taken as an example in the present application, and the main improvement is a pump body assembly of the compressor.

As shown in fig. 4, the relief via hole 100 is disposed concentrically with the lower flange 60, and the relief ring groove 61 is disposed eccentrically with the lower flange 60. In this way, the communication reliability of the relief ring groove 61 to the two limiting chambers 321 is ensured.

As shown in fig. 3 and 6, the second limiting passage 32 directly penetrates through the end face of the cross groove structure 30 along the axial direction of the cross groove structure 30, so that one end of the cross groove structure 30 is open, an opening 33 for the crankshaft 10 to extend is reserved on the end face of the end of the cross groove structure 30 which is not open, the opening 33 is concentrically arranged with the cross groove structure 30, and the opening 33 is communicated with the first limiting passage 31.

In this application, considering that the second limiting channel 32 directly penetrates through the end face of the cross groove structure 30 along the axial direction of the cross groove structure 30, so that the end of the cross groove structure 30 with the second limiting channel 32 is open, the height of the first limiting channel 31 in the axial direction of the cross groove structure 30 is set higher than the height of the second limiting channel 32 in the axial direction of the cross groove structure 30, so as to prevent leakage, as shown in fig. 1, 3 and 5, the height of the first eccentric portion 11 in the axial direction of the crankshaft 10 is greater than the height of the second eccentric portion 12 in the axial direction of the crankshaft 10. In this way, the assembling feasibility between the crankshaft 10 and the cross groove structure 30 is ensured.

As shown in fig. 4 and 5, the inner diameter D1 of the relief ring groove 61, the outer diameter D2 of the relief ring groove 61, and the diameter D5 of the shaft body portion of the crankshaft 10 on the side of the second eccentric portion 12 away from the first eccentric portion 11 satisfy: D1-D5 is less than or equal to 1mm and less than or equal to D2. Thus, it is ensured that the two limiting cavities 321 can be effectively communicated through the pressure relief ring groove 61, so that the problem of pressure oil in the limiting cavities 321 is solved.

As shown in fig. 4 and 6, the cross groove structure 30 has a central hole 34, the central hole 34 is used for communicating the first limiting channel 31 and the second limiting channel 32, and the outer circle diameter D2 of the pressure relief ring groove 61, the hole diameter D3 of the central hole 34, and the outer circle diameter D4 of the cross groove structure 30 satisfy: D4-D2 is more than or equal to 0.1mm and less than or equal to D3. Thus, it is ensured that the two limiting cavities 321 can be effectively communicated through the pressure relief ring groove 61, so that the problem of pressure oil in the limiting cavities 321 is solved.

Alternatively, the groove section of the pressure relief ring groove 61 is one of circular, square, and elliptical.

As shown in fig. 11, at least one oil drain hole 611 is formed on the bottom surface of the pressure relief ring groove 61, and the oil drain hole 611 penetrates through the end surface of the lower flange 60 on the side away from the cylinder liner 20, so that the oil drain hole 611 communicates with the outside. In this way, it is ensured that the refrigerant oil stored in the relief ring groove 61 can be directly discharged to the outside of the pump body assembly through the oil drain hole 611.

Further, as shown in fig. 11, a drain hole 611 is opened at the bottom surface of the groove on the distal end side of the relief ring groove 61. In this way, the hole cross section of the oil drain hole 611 is ensured to be as large as possible, and the reliability of the seal of the pump body assembly is ensured while the reliability of the discharge of the frozen oil is ensured.

In this application, the first eccentric portion 11 and the second eccentric portion 12 have a phase difference of a first included angle a, the eccentric amount of the first eccentric portion 11 is equal to the eccentric amount of the second eccentric portion 12, and the extending direction of the first limiting channel 31 and the extending direction of the second limiting channel 32 have a phase difference of a second included angle B, wherein the first included angle a is twice the second included angle B.

Preferably, the first eccentric portion 11 and the second eccentric portion 12 are disposed 180 ° opposite each other.

As shown in fig. 3, the projection of the slider 40 in the sliding direction thereof is circular, the projection of the first limiting passage 31 in the sliding direction of the slider 40 is circular,

of course, other ways of achieving the purpose of communicating the two limiting chambers 321 may be provided, for example, by providing a crankshaft countersink 13 (see fig. 12) on the end face of the second eccentric portion 12 of the crankshaft 10 on the side facing the lower flange 60, or providing an eccentric portion countersink 121 (see fig. 12) at the proximal end of the second eccentric portion 12, or providing a chamfer at the edge of the end face of the second eccentric portion 12 of the crankshaft 10 on the side facing the lower flange 60, or providing a countersink on the channel wall of the second limiting channel 32 of the cross channel structure 30.

It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.

The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present invention unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.

Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.

It should be noted that the terms "first," "second," and the like in the description and claims of the present application and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate such that embodiments of the present application described herein may be implemented in sequences other than those illustrated or described herein.

The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (12)

1. A fluid machine, comprising:

a crankshaft (10), wherein the crankshaft (10) is provided with a first eccentric part (11) and a second eccentric part (12) along the axial direction thereof;

the crankshaft (10) and the cylinder sleeve (20) are eccentrically arranged, and the eccentricity is fixed;

the cross groove structure (30), the cross groove structure (30) is rotatably arranged in the cylinder sleeve (20), the cross groove structure (30) is provided with a first limiting channel (31) and a second limiting channel (32), the first limiting channel (31) and the second limiting channel (32) are sequentially arranged along the axial direction of the crankshaft (10), the first limiting channel (31) is positioned above the second limiting channel (32), the extending direction of the first limiting channel (31) and the second limiting channel (32) is perpendicular to the axial direction of the crankshaft (10), the second eccentric part (12) is slidably arranged in the second limiting channel (32) and forms a limiting cavity (321), and the limiting cavity (321) is positioned in the sliding direction of the second eccentric part (12);

the sliding block (40) is provided with a through hole (41), the first eccentric part (11) stretches into the through hole (41), the sliding block (40) is slidably arranged in the first limiting channel (31) and forms a variable volume cavity, the variable volume cavity is positioned in the sliding direction of the sliding block (40), the crankshaft (10) rotates to drive the sliding block (40) to reciprocally slide in the first limiting channel (31) and interact with the cross groove structure (30), so that the cross groove structure (30) and the sliding block (40) rotate in the cylinder sleeve (20);

go up flange (50) and lower flange (60), go up flange (50) with lower flange (60) set up respectively the axial both ends of cylinder liner (20), go up flange (50) with all offer on lower flange (60) and be used for dodging via hole (100) of bent axle (10), lower flange (60) orientation offer relief groove (61) on the terminal surface of cylinder liner (20) one side, just relief groove (61) are located dodge via hole (100) periphery side, relief groove (61) are used for the intercommunication two spacing chamber (321).

2. The fluid machine according to claim 1, characterized in that the relief via (100) is arranged concentrically with the lower flange (60) and the relief ring groove (61) is arranged eccentrically with the lower flange (60).

3. The fluid machine according to claim 1, characterized in that the height of the first eccentric portion (11) in the axial direction of the crankshaft (10) is greater than the height of the second eccentric portion (12) in the axial direction of the crankshaft (10).

4. The fluid machine according to claim 1, wherein the second limiting passage (32) directly penetrates through to the end face of the cross groove structure (30) along the axial direction of the cross groove structure (30) so that one end of the cross groove structure (30) is open, an opening (33) for the crankshaft (10) to extend out is reserved on the end face of the end of the cross groove structure (30) which is not open, the opening (33) is concentrically arranged with the cross groove structure (30), and the opening (33) is communicated with the first limiting passage (31).

5. The fluid machine according to claim 1, characterized in that between the inner diameter D1 of the relief ring groove (61), the outer diameter D2 of the relief ring groove (61), the diameter D5 of the shaft body portion of the crankshaft (10) on the side of the second eccentric portion (12) remote from the first eccentric portion (11) is satisfied: D1-D5 is less than or equal to 1mm and less than or equal to D2.

6. The fluid machine according to claim 1, wherein the cross groove structure (30) has a central hole (34), the central hole (34) is used for communicating the first limiting channel (31) and the second limiting channel (32), and the outer circle diameter D2 of the pressure relief ring groove (61), the hole diameter D3 of the central hole (34) and the outer circle diameter D4 of the cross groove structure (30) satisfy: D4-D2 is more than or equal to 0.1mm and less than or equal to D3.

7. The fluid machine according to claim 1, wherein the groove cross section of the pressure relief ring groove (61) is one of circular, square, oval.

8. The fluid machine according to any one of claims 1 to 7, wherein at least one drain hole (611) is provided at the bottom surface of the relief ring groove (61), and the drain hole (611) penetrates through the end surface of the lower flange (60) on the side away from the cylinder liner (20), so that the drain hole (611) communicates with the outside.

9. The fluid machine according to claim 8, wherein the oil drain hole (611) is opened at a bottom surface of the groove on a distal end side of the pressure relief ring groove (61).

10. The fluid machine according to any one of claims 1 to 7, characterized in that the first eccentric portion (11) and the second eccentric portion (12) have a phase difference of a first angle a, the eccentric amount of the first eccentric portion (11) being equal to the eccentric amount of the second eccentric portion (12), the extending direction of the first limiting channel (31) and the extending direction of the second limiting channel (32) have a phase difference of a second angle B, wherein the first angle a is twice the second angle B.

11. The fluid machine according to claim 10, characterized in that the first eccentric portion (11) and the second eccentric portion (12) are arranged 180 ° opposite each other.

12. A heat exchange device comprising a fluid machine according to any one of claims 1 to 11.