CN222276940U - Fluid machine and heat exchange device - Google Patents

Abstract

The utility model provides a fluid machinery and heat exchange equipment, the fluid machinery includes a crankshaft, a cylinder sleeve, a cross groove structure, a slider, an upper flange and a lower flange, the crankshaft is provided with a first eccentric part and a second eccentric part along its axial direction; the crankshaft and the cylinder sleeve are eccentrically arranged; the cross groove structure is rotatably arranged in the cylinder sleeve, the first limiting channel and the second limiting channel of the cross groove structure are sequentially arranged along the axial direction of the crankshaft, the extension 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; the first eccentric part extends into the through hole of the slider, the slider is slidably arranged in the first limiting channel and forms a variable volume cavity; the upper flange and the lower flange are respectively arranged at the axial ends of the cylinder sleeve, and a pressure relief ring groove is opened on the end surface of the lower flange facing the cylinder sleeve, and the pressure relief ring groove is used to connect the two limiting cavities. The utility model solves the problems of low energy efficiency and high power consumption of compressors in the prior art.

Description

Fluid machine and heat exchange device

Technical Field

The utility model 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 utility model

The utility model 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 utility model, 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 along an axial direction thereof, the crankshaft is eccentrically disposed with the cylinder liner and has a fixed eccentricity, the cross groove structure is rotatably disposed in the cylinder liner, the cross groove structure has a first limit channel and a second limit channel, the first limit channel and the second limit channel are sequentially disposed along the axial direction of the crankshaft, the first limit channel is located above the second limit channel, an extending direction of the first limit channel and the second limit channel is perpendicular to the axial direction of the crankshaft, the second eccentric portion is slidably disposed in the second limit channel and forms a limit cavity, the limit cavity is located in a sliding direction of the second eccentric portion, the slider is extended into the through hole, the slider is slidably disposed in the first limit channel and forms a variable volume cavity, the cross groove structure is rotated to drive the slider to reciprocally slide in the first limit channel and interact with the cross groove structure, so that the extending direction of the first limit channel is perpendicular to the axial direction of the crankshaft, the cross groove structure is disposed at both sides of the upper flange and the lower flange are disposed at opposite sides of the upper flange and the lower flange, the upper flange is formed to be opposite to the upper flange, and the lower flange is formed to the lower flange, and the upper flange is opened to the upper side of the relief hole, and the relief hole is formed.

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 that D1-D5 is less than or equal to 1mm.

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 are 0.1 mm-D4-D2-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 utility model, 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, the fluid machinery provided by the application can stably run, namely, the energy efficiency of the compressor is ensured to be higher, 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 utility model and are incorporated in and constitute a part of this specification, illustrate embodiments of the utility model and together with the description serve to explain the utility model. 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 utility model;

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 utility model;

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 part, 12, a second eccentric part, 121, an eccentric part sink, 13, a crankshaft sink;

20. Cylinder sleeve;

30. A cross slot structure; 31, a first limiting channel, 32, a second limiting channel, 321, a limiting cavity, 33, an opening, 34 and a center hole;

40. The sliding block, 41, the through hole, 50, the upper flange;

60. the device comprises a lower flange, a pressure relief ring groove, 611 and a drain hole;

100. avoiding the via hole.

Detailed Description

The following description of the embodiments of the present utility model 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 utility model, 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 utility model, its application, or uses. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.

It should be noted that, the two cylinders of the compressor of the double-cylinder rotary cylinder piston are symmetrically arranged at 180 degrees, so that the change of the load torque tends to be gentle, and therefore the vibration of the compressor is very small, but due to the defect of the compressor, the leakage loss of the gas of the compressor is very high, while the leakage loss of the gas of the compressor of the single-cylinder rotary cylinder piston is small, but the torque peak value is very large, the vibration quantity of the compressor is also relatively 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 volume and changed into a torque balancing device for use, so as not to participate in the suction and exhaust of the compressor, thereby creating a new structural form, hereinafter referred to as a single-cylinder limiting device, and a great number of experiments show that the single-cylinder limiting device inherits the advantages of double cylinders and single cylinders at the same time, further expands the advantages of the rotary cylinder compressor, and simultaneously, the corresponding problems are accompanied that when the compressor is in operation, the refrigerating oil in the oil pool can be 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 suction and exhaust, so that the refrigerating oil in the cross groove structure 30 can obstruct the rotation of the crankshaft 10, thereby increasing the power consumption of the compressor.

In order to solve the problems of low energy efficiency and high power consumption of the compressor in the prior art, the utility model 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 comprises a crankshaft 10, a cylinder sleeve 20, a cross groove structure 30, a sliding block 40, an upper flange 50 and a lower flange 60, wherein the crankshaft 10 is axially provided with a first eccentric part 11 and a second eccentric part 12, the crankshaft 10 and the cylinder sleeve 20 are eccentrically arranged and have fixed eccentric distances, 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, 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 sliding block 40 is positioned in the sliding direction of the sliding sleeve 40, the sliding block 40 is positioned above the second limiting channel 32, the sliding channel 40 is axially opposite to the first limiting channel 40, the sliding groove 40 is axially drives the sliding block 40, the sliding block 40 is axially passes through the annular groove 40 and the lower flange 60, and is axially arranged at the two sides of the flange 60, and is axially opposite to the flange 50 is axially arranged at the side of the flange 60, and is opposite to the side of the flange 50, and is axially opposite to the flange 60, and is opposite to the side to the upper flange 60, and is opposite to the side of the upper flange 60, and is axially opposite to the side to the lower flange, and is opposite to the side.

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, the fluid machinery provided by the application can stably run, namely, the energy efficiency of the compressor is ensured to be higher, so that the working reliability of the heat exchange equipment is ensured.

In the present application, unlike the rotor compressor, the compressor of the present application is designed such that there is an eccentric space between the cylinder liner 20 and the crankshaft 10, and the crankshaft 10 drives the sliding block 40 and the cross groove structure 30 to rotate in the cylinder liner 20 when the compressor is operated, and the cross groove structure 30 and the crankshaft 10 rotate around the respective centers, and the sliding block 40 reciprocates simultaneously with respect to the cross groove structure 30 and the crankshaft 10, as shown in fig. 1, 2, and 7 to 10. The reciprocating motion of the sliding block 40 relative to the cross groove structure 30 realizes the periodical enlargement and reduction of the variable volume cavity, the circular motion of the cross groove structure 30 relative to the cylinder sleeve 20 realizes the communication of the variable volume cavity with the air suction channel and the air discharge channel respectively, and the two composite motions realize the air suction, compression and air discharge 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.

In the present application, the fluid machine includes a compressor, and the present application uses the compressor as an example, 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 the present application, since the second stopper passage 32 is formed to extend directly through the end face of the intersecting groove structure 30 in the axial direction of the intersecting groove structure 30 so that the end of the intersecting groove structure 30 having the second stopper passage 32 is open, the height of the first stopper passage 31 in the axial direction of the intersecting groove structure 30 is set higher than the height of the second stopper passage 32 in the axial direction of the intersecting groove structure 30 to prevent leakage, and 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 larger 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 FIGS. 4 and 5, the diameter D1 of the inner circumference of the relief ring groove 61, the diameter D2 of the outer circumference 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 that 1 mm.ltoreq.D1-D5.ltoreq.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 is provided with 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 meet that 0.1mm is less than or equal to D4-D2 is 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 the present application, 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 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 angle B, wherein the first angle a is twice the second 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 exemplary embodiments according to 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 utility model 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 refer to 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," "upper" and "upper surface," "above" and the like, may be used herein for ease of description to describe one device or feature's spatial relationship 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 process is carried out, the exemplary term "above" may be included. Upper and lower. Two orientations 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 exemplary embodiments according to 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 the 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 application described herein may be implemented in sequences other than those illustrated or otherwise described herein.

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

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, wherein a diameter D5 of a shaft body portion of the crankshaft (10) on a side of the second eccentric portion (12) away from the first eccentric portion (11) between an inner diameter D1 of the relief ring groove (61), an outer diameter D2 of the relief ring groove (61), and a diameter D5 of 1mm 1-D5-D2 are satisfied.

6. The fluid machine according to claim 1, wherein the cross groove structure (30) has a center hole (34), the center 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 center hole (34) and the outer circle diameter D4 of the cross groove structure (30) satisfy that 0.1mm is less than or equal to D4-D2 is 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.