Fluid machine and heat exchange device

Abstract

The utility model provides a fluid machine and heat exchange equipment, the fluid machine comprises a crankshaft, a cylinder sleeve, a cross groove structure, a sliding block, an upper flange and a lower flange, the crankshaft is provided with a first eccentric part and a second eccentric part along the axial direction; 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 in 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 a through hole of the sliding block, and the sliding block is arranged in the first limiting channel in a sliding mode and forms a variable volume cavity. The upper flange and the lower flange are arranged at the two axial ends of the cylinder sleeve correspondingly, and a pressure relief ring groove is formed in the end face of the side, facing the cylinder sleeve, of the lower flange and used for communicating the two limiting cavities. According to the utility model, the problems of low energy efficiency and high power consumption of the compressor in the prior art are solved.

Description

Technical Field

[0001] The utility model relates to the technical field of heat exchange systems, in particular to a fluid machinery and a heat exchange device. Background Art

[0002] The fluid machinery in the prior art includes compressors and expanders, etc. Take the compressor as an example.

[0003] According to the national energy conservation and environmental protection policies and consumers' requirements for air conditioning comfort, the air conditioning industry has been pursuing high efficiency and low noise. The compressor, as the heart of the air conditioner, has a direct impact on the energy efficiency and noise level of the air conditioner. As the mainstream household air conditioning compressor, the rolling rotor compressor has been relatively mature after nearly a hundred years of development. It is limited by the structural principle and has limited room for optimization. If a major breakthrough is to be achieved, innovation in structural principles is required.

[0004] Therefore, there is an urgent need to propose a compressor with the characteristics of high energy efficiency and low noise. Utility Model Content

[0005] The main purpose of the utility model is to provide a fluid machinery and a heat exchange device to solve the problems of low energy efficiency and high power consumption of compressors in the prior art.

[0006] In order to achieve the above-mentioned purpose, according to one aspect of the utility model, a fluid machinery is provided, 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 its axial direction; the crankshaft and the cylinder liner are eccentrically arranged and the eccentricity is fixed; the cross-groove structure is rotatably arranged in the cylinder liner, and the cross-groove structure has 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, and the first limiting channel is located above the second limiting channel, and the extension direction of the first limiting channel and the second limiting channel is perpendicular to the axial direction of the crankshaft, and the second eccentric portion is slidably arranged in the second limiting channel and forms a The first eccentric portion extends into the through hole, and the slider is slidably arranged in the first limiting channel to form a variable volume chamber, and the variable volume chamber is located in the sliding direction of the slider. The crankshaft rotates to drive the slider to slide back and forth in the first limiting channel while interacting with the cross groove structure to make the cross groove structure and the slider rotate in the cylinder sleeve; the upper flange and the lower flange are respectively arranged at the axial ends of the cylinder sleeve, and the upper flange and the lower flange are both provided with avoidance holes for avoiding the crankshaft, and a pressure relief ring groove is provided on the end surface of the lower flange facing the cylinder sleeve, and the pressure relief ring groove is located on the outer peripheral side of the avoidance hole, and the pressure relief ring groove is used to connect the two limiting chambers.

[0007] Furthermore, the avoidance hole is concentrically arranged with the lower flange, and the pressure relief ring groove is eccentrically arranged with the lower flange.

[0008] Further, a height of the first eccentric portion in the axial direction of the crankshaft is greater than a height of the second eccentric portion in the axial direction of the crankshaft.

[0009] Furthermore, the second limiting channel directly penetrates through the cross-groove structure along the axial direction to the end face of the cross-groove structure so that one end of the cross-groove structure is open, and the end face of the cross-groove structure that is not open is provided with an opening for the crankshaft to extend out, and the opening is concentrically arranged with the cross-groove structure, and the opening is connected to the first limiting channel.

[0010] Furthermore, 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 crankshaft body portion located on the side of the second eccentric portion away from the first eccentric portion satisfy: 1mm≤D1-D5≤D2.

[0011] Furthermore, the cross groove structure has a center hole, which is used to connect the first limiting channel and the second limiting channel. The outer circle diameter D2 of the pressure relief ring groove, the hole diameter D3 of the center hole, and the outer circle diameter D4 of the cross groove structure satisfy: 0.1mm≤D4-D2≤D3.

[0012] Furthermore, the cross section of the pressure relief ring groove is one of circular, square and elliptical.

[0013] Furthermore, at least one oil drain hole is formed on the bottom surface of the pressure relief ring groove, and the oil drain hole passes through the end surface of the lower flange away from the cylinder liner, so that the oil drain hole is connected with the outside.

[0014] Furthermore, the oil drain hole is formed at the groove bottom surface at the distal end side of the pressure relief ring groove.

[0015] Furthermore, there is a phase difference of a first angle A between the first eccentric portion and the second eccentric portion, the eccentricity of the first eccentric portion is equal to the eccentricity of the second eccentric portion, and there is a phase difference of a second angle B between the extension direction of the first limiting channel and the extension direction of the second limiting channel, wherein the first angle A is twice the second angle B.

[0016] Furthermore, the first eccentric portion and the second eccentric portion are arranged opposite to each other at an angle of 180 degrees.

[0017] According to another aspect of the present invention, a heat exchange device is provided, comprising a fluid machine, wherein the fluid machine is the above-mentioned fluid machine.

[0018] By applying the technical solution of the utility model, the cross-groove structure is arranged to have a first limiting channel and a second limiting channel. At the same time, the second eccentric part is slidably arranged in the second limiting channel to form a limiting cavity, and the limiting cavity is located in the sliding direction of the second eccentric part. In addition, the slider is slidably arranged in the first limiting channel to form a variable volume cavity, and the variable volume cavity is located in the sliding direction of the slider. The crankshaft rotates to drive the slider to slide back and forth in the first limiting channel while interacting with the cross-groove structure to make the cross-groove structure and the slider rotate in the cylinder liner. In this way, the dead point position of the fluid machinery is avoided, the movement reliability of the fluid machinery is improved, and the working reliability of the heat exchange equipment is ensured.

[0019] It should be noted that by opening a pressure relief ring groove on the end face of the lower flange facing the cylinder liner, the pressure relief ring groove is connected to the two limit chambers, which makes it easy to discharge the refrigerant oil in time, thereby ensuring the rotation reliability of the crankshaft and avoiding increasing the power consumption of the fluid machinery.

[0020] Furthermore, since the fluid machinery provided by the present application can operate stably, that is, the energy efficiency of the compressor is ensured to be high, thereby ensuring the working reliability of the heat exchange equipment. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The drawings constituting part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation on the present invention. In the drawings:

[0022] Figure 1 A schematic structural diagram of a pump assembly of a compressor according to an optional embodiment of the utility model is shown;

[0023] Figure 2 Shows Figure 1 Schematic diagram of the cross-sectional structure from the CC perspective;

[0024] Figure 3 Shows Figure 1 Schematic diagram of the exploded structure of the pump assembly;

[0025] Figure 4 Shows Figure 1 A schematic diagram of the structure of the lower flange of the pump body assembly;

[0026] Figure 5 Shows Figure 3 A schematic diagram of the structure of the crankshaft of the pump assembly;

[0027] Figure 6 Shows Figure 3 A schematic cross-sectional view of the cross-groove structure of the pump assembly;

[0028] Figure 7 Shows Figure 1 A schematic cross-sectional structural diagram of a pump body assembly in FIG. 1 , wherein a schematic structural diagram of a state when the crankshaft drives the cross groove structure to rotate 0° is shown;

[0029] Figure 8 Shows Figure 7 A schematic diagram of the state structure when the crankshaft drives the cross groove structure to rotate 90°;

[0030] Fig. 9 Shows Figure 8 A schematic diagram of the state structure when the crankshaft drives the cross groove structure to rotate 180°;

[0031] Fig.10 Shows Fig. 9 A schematic diagram of the state structure when the crankshaft drives the cross slot structure to rotate 270°;

[0032] Fig.11 A schematic structural diagram of a lower flange of a pump body assembly according to another optional embodiment of the utility model is shown;

[0033] Fig.12 Shows Figure 3 Schematic diagram of the structure of the crankshaft of the pump body assembly.

[0034] The above drawings include the following reference numerals:

[0035] 10. crankshaft; 11. first eccentric portion; 12. second eccentric portion; 121. eccentric portion sink groove; 13. crankshaft sink groove;

[0036] 20. Cylinder liner;

[0037] 30. cross groove structure; 31. first limiting channel; 32. second limiting channel; 321. limiting cavity; 33. opening; 34. center hole;

[0038] 40. Slider; 41. Through hole; 50. Upper flange;

[0039] 60, lower flange; 61, pressure relief ring groove; 611, oil drain hole;

[0040] 100. Avoid vias. DETAILED DESCRIPTION

[0041] The following will be combined with the drawings in the embodiments of the utility model to clearly and completely describe the technical solutions in the embodiments of the utility model. Obviously, the described embodiments are only part of the embodiments of the utility model, not all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means a limitation on the utility model and its application or use. Based on the embodiments in the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0042] It should be noted that the two cylinders of the double-cylinder rotary piston compressor are arranged symmetrically at 180°, which can make the change of load torque tend to be smooth, so the vibration of the compressor is very small. However, due to its own defects, the gas leakage loss of the above compressor is also very high; while the gas leakage loss of the single-cylinder rotary piston compressor is smaller, but the torque peak is large, the vibration of the compressor is also relatively large, and when the pump body of the single-cylinder rotary piston compressor rotates to a certain angle, the torque is zero, resulting in the compressor being unable to start at this rotation angle.

[0043] In order to solve the above problems, the volume of the second limiting channel 32 of the twin-cylinder compressor can be reduced and used as a torque balancing device instead, which does not participate in the suction and exhaust of the compressor. Thus, a new structural form is born, hereinafter referred to as a single-cylinder limiting device. A large number of experiments have shown that this single-cylinder limiting device inherits the advantages of both twin-cylinder and single-cylinder compressors, and further expands the advantages of the rotary cylinder compressor; at the same time, some corresponding problems are also brought about, that is, when the compressor is running, the refrigerant oil in the oil pool will be transported to the various friction pairs inside the pump body assembly through the central oil hole on the crankshaft 10. Since the second limiting channel 32 does not participate in the suction and exhaust, the refrigerant oil in the cross-groove structure 30 cannot be discharged in time. At this time, the refrigerant oil in the cross-groove structure 30 will hinder the rotation of the crankshaft 10, thereby increasing the power consumption of the compressor.

[0044] In order to solve the problems of low energy efficiency and high power consumption of compressors in the prior art, the utility model provides a fluid machinery and a heat exchange device. The heat exchange device includes a fluid machinery, and the fluid machinery is the fluid machinery described above and below.

[0045] like Figures 1 to 12As shown, the fluid machinery 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 along its axial direction; the crankshaft 10 and the cylinder liner 20 are eccentrically arranged and the eccentricity is fixed; the cross groove structure 30 is rotatably arranged in the cylinder liner 20, and the cross groove structure 30 has 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, and the first limiting channel 31 is located above the second limiting channel 32, and the extension direction of the first limiting channel 31 and the second limiting channel 32 is perpendicular to the axial direction of the crankshaft 10, and the second eccentric portion 12 is slidably arranged in the second limiting channel 32 and forms a limiting cavity 321, and the limiting cavity 321 is located at the second eccentric In the sliding direction of the part 12; the slider 40 has a through hole 41, the first eccentric part 11 extends into the through hole 41, the slider 40 is slidably arranged in the first limiting channel 31 and forms a variable volume chamber, the variable volume chamber is located in the sliding direction of the slider 40, the crankshaft 10 rotates to drive the slider 40 to slide back and forth in the first limiting channel 31 while interacting with the cross groove structure 30, so that the cross groove structure 30 and the slider 40 rotate in the cylinder sleeve 20; the upper flange 50 and the lower flange 60 are respectively arranged at the axial ends of the cylinder sleeve 20, and the upper flange 50 and the lower flange 60 are both provided with avoidance holes 100 for avoiding the crankshaft 10, and the end surface of the lower flange 60 facing the cylinder sleeve 20 is provided with a pressure relief ring groove 61, and the pressure relief ring groove 61 is located on the outer peripheral side of the avoidance hole 100, and the pressure relief ring groove 61 is used to connect the two limiting chambers 321.

[0046] By setting the cross-groove structure 30 to have a first limiting channel 31 and a second limiting channel 32, at the same time, the second eccentric portion 12 is slidably set in the second limiting channel 32 and forms a limiting cavity 321, and the limiting cavity 321 is located in the sliding direction of the second eccentric portion 12. In addition, the slider 40 is slidably set in the first limiting channel 31 and forms a variable volume cavity, and the variable volume cavity is located in the sliding direction of the slider 40. The crankshaft 10 rotates to drive the slider 40 to slide back and forth in the first limiting channel 31 while interacting with the cross-groove structure 30, so that the cross-groove structure 30 and the slider 40 rotate in the cylinder liner 20. In this way, the dead point position of the fluid machinery is avoided, the movement reliability of the fluid machinery is improved, and the working reliability of the heat exchange equipment is ensured.

[0047] It should be noted that by opening a pressure relief ring groove 61 on the end face of the lower flange 60 facing the cylinder liner 20, the pressure relief ring groove 61 is connected to the two limit chambers 321, so that the refrigerant oil can be discharged in time, thereby ensuring the rotation reliability of the crankshaft 10 and avoiding increasing the power consumption of the fluid machinery.

[0048] Furthermore, since the fluid machinery provided by the present application can operate stably, that is, the energy efficiency of the compressor is ensured to be high, thereby ensuring the working reliability of the heat exchange equipment.

[0049] It should be noted that in this application, Figure 1 , Figure 2 , Figures 7 to 10 As shown, unlike the rotary compressor, the compressor of the present application has an eccentric design between the cylinder sleeve 20 and the crankshaft 10. When the compressor is running, the crankshaft 10 drives the slider 40 and the cross groove structure 30 to rotate in the cylinder sleeve 20, and the cross groove structure 30 and the crankshaft 10 rotate around their respective centers, and the slider 40 reciprocates simultaneously relative to the cross groove structure 30 and the crankshaft 10. The reciprocating motion of the slider 40 relative to the cross groove structure 30 realizes the periodic enlargement and reduction of the variable volume chamber; and the circular motion of the cross groove structure 30 relative to the cylinder sleeve 20 realizes the communication between the variable volume chamber and the intake channel and the exhaust channel respectively; the above two composite motions realize the intake, compression and exhaust process of the compressor. The second limiting channel 32 cooperates with the second eccentric part 12 to form a limiting chamber 321, and there will also be periodic enlargement and reduction of the cavity, but the limiting chamber 321 does not have a matching intake and exhaust channel, so it does not participate in compression.

[0050] Usually, a certain amount of refrigerant oil is added to the compressor to dissipate heat and lubricate the pump assembly. The refrigerant oil level usually overflows the cylinder liner 20. In addition, the central oil hole of the crankshaft 10 continuously supplies oil to the friction pairs of the pump assembly. Therefore, the limit cavity 321 is often full of oil. However, oil is incompressible, and the gaps between the friction pairs are very small, so it is difficult for the oil to transfer. Then the rotational resistance of the second eccentric part 12 will increase, thereby increasing the power consumption of the compressor. Therefore, a technical solution of connecting the two limit cavities 321 is proposed.

[0051] It should be noted that, in the present application, the fluid machinery includes a compressor. The present application takes the compressor as an example, and the main improvement is in the pump body assembly of the compressor.

[0052] like Figure 4 As shown, the avoidance hole 100 is concentrically arranged with the lower flange 60, and the pressure relief ring groove 61 is eccentrically arranged with the lower flange 60. In this way, the reliability of the connection between the pressure relief ring groove 61 and the two limiting cavities 321 is ensured.

[0053] like Figure 3 and Figure 6 As shown, the second limiting channel 32 directly penetrates through the cross-groove structure 30 along the axial direction to the end face of the cross-groove structure 30 so that one end of the cross-groove structure 30 is open, and the end face of the cross-groove structure 30 that is not open is reserved with an opening 33 for the crankshaft 10 to extend out, and the opening 33 is concentrically arranged with the cross-groove structure 30, and the opening 33 is connected to the first limiting channel 31.

[0054] It should be noted that, in the present application, considering that the second limiting channel 32 directly penetrates to the end surface 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 having the second limiting channel 32 is open, therefore, 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 to prevent leakage, such as Figure 1 , Figure 3 , Figure 5 As shown, 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 assembly feasibility between the crankshaft 10 and the cross groove structure 30 is ensured.

[0055] like Figure 4 and Figure 5 As shown, the inner diameter D1 of the pressure relief ring groove 61, the outer diameter D2 of the pressure relief ring groove 61, and the diameter D5 of the shaft body portion of the crankshaft 10 located on the side of the second eccentric portion 12 away from the first eccentric portion 11 satisfy the following relationship: 1mm≤D1-D5≤D2. In this way, the two limiting cavities 321 can be effectively connected through the pressure relief ring groove 61, which helps to solve the problem of oil pressure in the limiting cavity 321.

[0056] like Figure 4 and Figure 6 As shown, the cross groove structure 30 has a center hole 34, and the center hole 34 is used to connect the first limiting channel 31 and the second limiting channel 32. The outer diameter D2 of the pressure relief ring groove 61, the hole diameter D3 of the center hole 34, and the outer diameter D4 of the cross groove structure 30 meet the following conditions: 0.1mm≤D4-D2≤D3. In this way, it is ensured that the two limiting cavities 321 can be effectively connected through the pressure relief ring groove 61, which is conducive to solving the problem of oil pressure in the limiting cavity 321.

[0057] Optionally, the cross section of the pressure relief ring groove 61 is one of circular, square and elliptical.

[0058] like Fig.11 As shown, 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 passes through the end surface of the lower flange 60 away from the cylinder sleeve 20, so that the oil drain hole 611 is connected to the outside. In this way, it is ensured that the refrigerant oil stored in the pressure relief ring groove 61 can be directly discharged to the outside of the pump body assembly through the oil drain hole 611.

[0059] Furthermore, if Fig.11As shown, the oil drain hole 611 is provided at the groove bottom surface of the distal end side of the pressure relief ring groove 61. In this way, the hole cross section of the oil drain hole 611 can be as large as possible, and while ensuring the discharge reliability of the refrigeration oil, the sealing reliability of the pump body assembly can also be ensured.

[0060] It should be noted that in the present application, there is a phase difference of a first angle A between the first eccentric portion 11 and the second eccentric portion 12, the eccentricity of the first eccentric portion 11 is equal to the eccentricity of the second eccentric portion 12, and there is a phase difference of a second angle B between the extension direction of the first limiting channel 31 and the extension direction of the second limiting channel 32, wherein the first angle A is twice the second angle B.

[0061] Preferably, the first eccentric portion 11 and the second eccentric portion 12 are disposed opposite to each other at an angle of 180°.

[0062] like Figure 3 As shown, the projection of the slider 40 in the sliding direction thereof is circular, and the projection of the first limiting channel 31 in the sliding direction of the slider 40 is circular.

[0063] Of course, other methods can also be provided to achieve the purpose of connecting the two limit cavities 321, for example, by opening a crankshaft groove 13 on the end surface of the second eccentric portion 12 of the crankshaft 10 facing the lower flange 60 (see Fig.12 ), or an eccentric portion sink groove 121 is provided at the proximal end of the second eccentric portion 12 (see Fig.12 ), or a chamfer is provided at the end surface edge of the second eccentric portion 12 of the crankshaft 10 facing the lower flange 60, or a recessed groove is provided on the channel wall of the second limiting channel 32 of the cross groove structure 30.

[0064] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0065] Unless otherwise specifically stated, the relative arrangement, numerical expressions and numerical values ​​of the parts and steps described in these embodiments do not limit the scope of the utility model. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the accompanying drawings are not drawn according to the actual proportional relationship. The technology, methods and equipment known to ordinary technicians in the relevant field may not be discussed in detail, but in appropriate cases, the technology, methods and equipment should be regarded as a part of the authorization specification. In all examples shown and discussed here, any specific value should be interpreted as merely exemplary, rather than as a limitation. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters represent similar items in the following drawings, so once a certain item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0066] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used here to describe the spatial positional relationship between a device or feature and other devices or features as shown in the figure. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figure. For example, if the device in the accompanying drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0067] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0068] It should be noted that the terms "first", "second", etc. in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the numbers used in this way can be interchanged where appropriate, so that the embodiments of the present application described herein can be implemented in an order other than those illustrated or described herein.

[0069] The above description is only the preferred embodiment of the utility model, and is not intended to limit the utility model. For those skilled in the art, the utility model can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the utility model shall be included in the protection scope of the utility model.

Claims

1. A fluid machine, characterized in that: include: A crankshaft (10), wherein the crankshaft (10) is provided with a first eccentric portion (11) and a second eccentric portion (12) along its axial direction; A cylinder sleeve (20), wherein the crankshaft (10) and the cylinder sleeve (20) are eccentrically arranged with a fixed eccentricity; A cross groove structure (30), wherein the cross groove structure (30) is rotatably arranged in the cylinder sleeve (20), and the cross groove structure (30) has a first limiting channel (31) and a second limiting channel (32), wherein the first limiting channel (31) and the second limiting channel (32) are sequentially arranged along the axial direction of the crankshaft (10), and the first limiting channel (31) is located above the second limiting channel (32), and the extension direction of the first limiting channel (31) and the second limiting channel (32) is perpendicular to the axial direction of the crankshaft (10), and the second eccentric portion (12) is slidably arranged in the second limiting channel (32) to form a limiting cavity (321), and the limiting cavity (321) is located in the sliding direction of the second eccentric portion (12); A slider (40), the slider (40) having a through hole (41), the first eccentric portion (11) extending into the through hole (41), the slider (40) being slidably disposed in the first limiting channel (31) and forming a variable volume chamber, the variable volume chamber being located in the sliding direction of the slider (40), the crankshaft (10) rotating to drive the slider (40) to slide back and forth in the first limiting channel (31) while interacting with the cross groove structure (30), so that the cross groove structure (30) and the slider (40) rotate in the cylinder sleeve (20); An upper flange (50) and a lower flange (60), wherein the upper flange (50) and the lower flange (60) are respectively arranged at two axial ends of the cylinder sleeve (20), and each of the upper flange (50) and the lower flange (60) is provided with an escape hole (100) for escaping the crankshaft (10), and a pressure relief ring groove (61) is provided on the end surface of the lower flange (60) facing the cylinder sleeve (20), and the pressure relief ring groove (61) is located on the outer peripheral side of the escape hole (100), and the pressure relief ring groove (61) is used to connect the two limit cavities (321).

2. The fluid machine according to claim 1, characterized in that: The avoidance hole (100) is arranged concentrically with the lower flange (60), and the pressure 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, characterized in that: The second limiting channel (32) directly penetrates the cross-groove structure (30) along the axial direction to the end face of the cross-groove structure (30), so that one end of the cross-groove structure (30) is open, and the end face of the cross-groove structure (30) that is not open is reserved with an opening (33) for the crankshaft (10) to extend out, and the opening (33) is concentrically arranged with the cross-groove structure (30), and the opening (33) is connected to the first limiting channel (31).

5. The fluid machine according to claim 1, characterized in that: The inner diameter D1 of the pressure relief ring groove (61), the outer diameter D2 of the pressure relief ring groove (61), and the diameter D5 of the shaft portion of the crankshaft (10) located on the side of the second eccentric portion (12) away from the first eccentric portion (11) satisfy the following relationship: 1 mm ≤ D1 - D5 ≤ D2.

6. The fluid machine according to claim 1, characterized in that: The cross groove structure (30) has a center hole (34), and the center hole (34) is used to connect the first limiting channel (31) and the second limiting channel (32). The outer diameter D2 of the pressure relief ring groove (61), the hole diameter D3 of the center hole (34), and the outer diameter D4 of the cross groove structure (30) satisfy the following relationship: 0.1 mm ≤ D4 - D2 ≤ D3.

7. The fluid machine according to claim 1, characterized in that: The cross section of the pressure relief ring groove (61) is one of a circular, square and elliptical shape.

8. The fluid machine according to any one of claims 1 to 7, characterized in that: At least one oil leakage hole (611) is formed on the bottom surface of the pressure relief ring groove (61), and the oil leakage hole (611) passes through the end surface of the lower flange (60) away from the cylinder sleeve (20), so that the oil leakage hole (611) is connected to the outside.

9. The fluid machine according to claim 8, characterized in that: The oil drain hole (611) is opened at the groove bottom surface on the 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: There is a phase difference of a first angle A between the first eccentric portion (11) and the second eccentric portion (12), the eccentricity of the first eccentric portion (11) is equal to the eccentricity of the second eccentric portion (12), and there is a phase difference of a second angle B between the extension direction of the first limiting channel (31) and the extension direction of the second limiting channel (32), 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 opposite to each other at an angle of 180 degrees.

12. A heat exchange device, characterized in that: The invention comprises a fluid machine, wherein the fluid machine is the fluid machine according to any one of claims 1 to 11.

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