CN221647163U - Fluid machinery and heat exchange equipment - 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 first slider and a second slider, the crankshaft has a first eccentric part and a second eccentric part; the crankshaft and the cylinder sleeve are eccentrically arranged and the eccentricity is fixed; the cross groove structure is rotatably arranged in the cylinder sleeve, and the first limiting channel and the second limiting channel of the cross groove structure are arranged in sequence along the axial direction of the crankshaft; the first eccentric part extends into the first through hole of the first slider, the first slider is slidably arranged in the first limiting channel and forms a first variable volume chamber; the second eccentric part extends into the second through hole of the second slider, the second slider is slidably arranged in the second limiting channel and forms a second variable volume chamber; wherein the second limiting channel directly penetrates to 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 open. The utility model solves the problem of low energy efficiency of compressors in the prior art.

Description

Fluid machinery and heat exchange equipment

Technical Field

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

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

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.

Therefore, there is an urgent need to propose a compressor with the characteristics of high energy efficiency and low noise.

Utility Model Content

The main purpose of the utility model is to provide a fluid machinery and a heat exchange device to solve the problem of low energy efficiency of compressors in the prior art.

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 first slider and a second slider, 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 arranged in sequence 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; the first slider has a first through hole, the first eccentric portion extends into the first through hole, the first slider is slidably arranged in the first limiting channel and forms a first variable capacitance The first variable volume chamber is located in the sliding direction of the first slider, and the crankshaft rotates to drive the first slider to slide back and forth in the first limiting channel while interacting with the cross-groove structure, so that the cross-groove structure and the first slider rotate in the cylinder sleeve; the second slider has a second through hole, and the second eccentric portion extends into the second through hole. The second slider is slidably arranged in the second limiting channel and forms a second variable volume chamber, and the second variable volume chamber is located in the sliding direction of the second slider, and the crankshaft rotates to drive the second slider to slide back and forth in the second limiting channel while interacting with the cross-groove structure, so that the cross-groove structure and the second slider rotate in the cylinder sleeve; wherein, the second limiting channel directly penetrates to 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 open.

Furthermore, the fluid machinery further comprises an upper flange and a lower flange, the upper flange and the lower flange are respectively arranged at two axial ends of the cylinder sleeve, and the end surface of the second eccentric portion facing the lower flange serves as a thrust surface.

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.

Further, a height of the first slider in the axial direction of the cylinder sleeve is greater than a height of the second slider in the axial direction of the cylinder sleeve.

Furthermore, an opening is reserved on the end surface of one end of the cross-groove structure that is not open, for the crankshaft to extend out. The opening is concentrically arranged with the cross-groove structure, and the opening is communicated with the first limiting channel.

Furthermore, the cross-groove structure has a center hole, which is used to connect the first limiting channel and the second limiting channel. The diameter D1 of the first eccentric portion, the diameter D2 of the second eccentric portion, and the diameter D4 of the center hole satisfy: the design range of D4-D1 is 0.1~5mm, and D1=D2.

Furthermore, the cross-groove structure has a center hole, which is used to connect the first limiting channel and the second limiting channel. The diameter D3 of the shaft body portion of the crankshaft located on the side of the second eccentric portion away from the first eccentric portion, the diameter D4 of the center hole, and the diameter D2 of the second eccentric portion satisfy: D3+2×e+2×L3=D2, D2+2L5=D4, wherein e is the eccentricity of the first eccentric portion, L3 is the third reserved gap between the outer surface of the shaft body portion of the crankshaft located on the side of the second eccentric portion away from the first eccentric portion and the outer surface at the proximal end of the second eccentric portion, and L5 is the fifth reserved gap between the second eccentric portion and the hole wall of the center hole when the second eccentric portion is concentric with the center hole.

Furthermore, the design range of the third reserved gap L3 is 0.05 mm to 3 mm.

Furthermore, the design range of the fifth reserved gap L5 is 0.05 mm to 5 mm.

Furthermore, the projection of the first sliding block in the sliding direction is circular, and the projection of the second sliding block in the sliding direction is square.

Furthermore, the width B1 of the second slider and the diameter D5 of the first slider satisfy: 0.5≤B1/D5≤1.5.

Further, the height H1 of the second slider and the diameter D5 of the first slider satisfy: 0.5≤H1/D5＜1. Further, a first reserved gap L1 is provided between the outer peripheral surface of the first slider and the channel wall of the first limiting channel, and the design range of the first reserved gap L1 is 0.008mm～0.05mm.

Furthermore, in a direction perpendicular to the sliding direction of the second slider, a second reserved gap L2 is provided between the outer surface of the second slider and the channel wall of the second limiting channel, and the design range of the second reserved gap L2 is 0.008 mm to 0.05 mm.

Furthermore, the contour line of the first limiting channel matches the outer contour line of the first sliding block, and the contour line of the second limiting channel matches the outer contour line of the second sliding block.

Furthermore, the channel wall of the second limiting channel has an arc transition angle R, and the angle range of the arc transition angle R is R≥3 mm.

Furthermore, a minimum sealing distance L between the first limiting channel and the second limiting channel satisfies: L≥2 mm.

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.

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

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.

By applying the technical solution of the utility model, a semi-closed dual-cylinder four-compression structure is provided. By setting the cross-groove structure to a structural form with a first limit channel and a second limit channel, the first slider is slidably set in the first limit channel to form a first variable volume chamber, and the first variable volume chamber is located in the sliding direction of the first slider. The crankshaft rotates to drive the first slider to slide back and forth in the first limit channel while interacting with the cross-groove structure, so that the cross-groove structure and the first slider rotate in the cylinder sleeve; in addition, the second slider is slidably set in the second limit channel to form a second variable volume chamber, and the second variable volume chamber is located in the sliding direction of the second slider. The crankshaft rotates to drive the second slider to slide back and forth in the second limit channel while interacting with the cross-groove structure, so that the cross-groove structure and the second slider rotate in the cylinder sleeve. 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.

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

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:

FIG1 shows a schematic structural diagram of a pump assembly of a compressor according to an optional embodiment of the utility model;

FIG2 shows a schematic diagram of the exploded structure of the pump assembly in FIG1 ;

FIG3 is a schematic structural diagram of a crankshaft of the pump assembly in FIG2 ;

FIG4 is a schematic diagram showing a top view of the crankshaft and cross groove structure of the pump assembly in FIG1 when they are in an assembled state;

FIG5 is a schematic structural diagram showing a top view of the shaft body portion and the second eccentric portion of the pump assembly in FIG1 ;

FIG6 is a schematic structural diagram showing the cross groove structure of the pump body assembly in FIG2 ;

FIG7 shows a schematic cross-sectional view of the cross-groove structure in FIG5 ;

FIG8 is a schematic structural diagram of a first slider of the pump assembly in FIG2 ;

FIG9 is a schematic structural diagram of a second slider of the pump assembly in FIG2 ;

FIG10 is a schematic structural diagram showing the crankshaft, the cross groove structure, the first slider, and the second slider of the pump assembly in FIG2 when they are in an assembled state;

FIG11 is a schematic cross-sectional view of the pump assembly in FIG1 at the first slider;

FIG. 12 is a schematic cross-sectional view of the pump assembly in FIG. 1 at the second slider.

The above drawings include the following reference numerals:

10. crankshaft; 11. first eccentric portion; 12. second eccentric portion;

20. Cylinder liner;

30. cross groove structure; 31. first limit channel; 311. first variable volume cavity; 32. second limit channel; 321. second variable volume cavity; 33. opening; 34. center hole;

40. a first slider; 41. a first through hole;

50, upper flange; 60, lower flange;

70. Second sliding block; 71. Second through hole.

DETAILED DESCRIPTION

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.

Existing rotary piston compressors are generally divided into two categories: single-cylinder and double-cylinder. Among them, the cylinder of the single-cylinder rotary piston compressor is an axially closed design (that is, the volume chamber is connected to the radial direction and is in a completely closed state in the axial direction), the gas leakage loss is small, and the cooling capacity of the compressor is high. However, the compressor of this structural form still retains the same single eccentric part design of the crankshaft as the single-cylinder rotor compressor, that is, the torque peak of the compressor is very large, and the vibration of the compressor is also relatively large. The two ends of the cylinder of the double-cylinder rotary piston compressor adopt an open design, and the crankshaft is a double eccentric part design. The torque peak of the compressor is greatly reduced. However, due to the large gas leakage caused by the open structure, the cooling capacity of the compressor is low. Based on this, the present application proposes a semi-closed double-cylinder four-compression structure.

In order to solve the problem of low energy efficiency of compressors in the prior art, the utility model provides a fluid machine and a heat exchange device. The heat exchange device includes a fluid machine, and the fluid machine is the fluid machine described above and below.

As shown in Figures 1 to 12, the fluid machinery includes a crankshaft 10, a cylinder sleeve 20, a cross groove structure 30, a first slider 40 and a second slider 70. 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 sleeve 20 are eccentrically arranged and the eccentricity is fixed; 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, 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; the first slider 40 has a first through hole 41, the first eccentric portion 11 extends into the first through hole 41, the first slider 40 is slidably arranged in the first limiting channel 31 and forms a first variable volume chamber 311, and the first variable volume chamber 311 is formed. 11 is located in the sliding direction of the first slider 40, the crankshaft 10 rotates to drive the first 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 first slider 40 rotate in the cylinder sleeve 20; the second slider 70 has a second through hole 71, the second eccentric portion 12 extends into the second through hole 71, the second slider 70 is slidably arranged in the second limiting channel 32 and forms a second variable volume chamber 321, the second variable volume chamber 321 is located in the sliding direction of the second slider 70, the crankshaft 10 rotates to drive the second slider 70 to slide back and forth in the second limiting channel 32 while interacting with the cross-groove structure 30, so that the cross-groove structure 30 and the second slider 70 rotate in the cylinder sleeve 20; wherein, the second limiting channel 32 directly penetrates 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.

The present application provides a semi-enclosed dual-cylinder four-compression structure, by setting the cross groove structure 30 to have a first limiting channel 31 and a second limiting channel 32, the first slider 40 is slidably set in the first limiting channel 31 and forms a first variable volume chamber 311, the first variable volume chamber 311 is located in the sliding direction of the first slider 40, the crankshaft 10 rotates to drive the first slider 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 first slider 40 are in the cylinder The second slider 70 is slidably arranged in the second limiting channel 32 to form a second variable volume chamber 321, and the second variable volume chamber 321 is located in the sliding direction of the second slider 70. The crankshaft 10 rotates to drive the second slider 70 to slide back and forth in the second limiting channel 32 while interacting with the cross groove structure 30, so that the cross groove structure 30 and the second slider 70 rotate in the cylinder sleeve 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.

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.

It should be noted that, in the present application, the first slider 40 is slidably arranged in the first limiting channel 31 and forms a first variable volume chamber 311. The first variable volume chamber 311 is located in the sliding direction of the first slider 40. Since the first slider 40 slides back and forth in the first limiting channel 31, there are two first variable volume chambers 311; similarly, there are also two second variable volume chambers 321 (specifically refer to Figures 10 to 11).

The present application achieves a differentiated design of the first limiting channel 31 and the second limiting channel 32 by configuring one end of the cross-groove structure 30 to be an open structure, that is, one end of the cross-groove structure 30 is open and the other end of the cross-groove structure 30 is closed, thereby ensuring the sealing reliability inside the pump body assembly of the compressor, thereby achieving the purpose of reducing the torque peak of the compressor, which is beneficial to improving the performance of the compressor.

As shown in Fig. 1 and Fig. 2, the fluid machine further includes an upper flange 50 and a lower flange 60, which are respectively arranged at the axial ends of the cylinder liner 20, and the end surface of the second eccentric portion 12 facing the lower flange 60 is used as a thrust surface. In this way, the end surface of the second eccentric portion 12 facing the lower flange 60 is used as a thrust surface, thereby ensuring that the entire rotating shaft system is supported.

It should be noted that, in the present application, considering that the second limiting channel 32 directly penetrates 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 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, as shown in Figures 1 to 3, 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. The height of the first slider 40 in the axial direction of the cylinder sleeve 20 is greater than the height of the second slider 70 in the axial direction of the cylinder sleeve 20. In this way, the adaptability of the first eccentric portion 11 extending into the first through hole 41 and the first slider 40 slidingly arranged in the first limiting channel 31 is ensured, and the adaptability of the second eccentric portion 12 extending into the second through hole 71 and the second slider 70 slidingly arranged in the second limiting channel 32 is ensured.

As shown in FIG7 , an opening 33 for the crankshaft 10 to extend out is reserved on the end surface of the cross groove structure 30 that is not open, 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. In this way, the assembly feasibility between the crankshaft 10 and the cross groove structure 30 is ensured.

It should be noted that in the present application, in order to ensure that the crankshaft 10 and the cross-groove structure 30 can be assembled normally and reduce the leakage between the shaft gaps, as shown in Figure 7, 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 diameter D1 of the first eccentric portion 11, the diameter D2 of the second eccentric portion 12, and the diameter D4 of the center hole 34 satisfy: the design range of D4-D1 is 0.1~5mm, and D1=D2.

It should be noted that in the present application, in order to ensure the feasibility of assembly between the crankshaft 10 and the cross-groove structure 30, the cross-groove structure 30 further has a center hole 34, and the center hole 34 is used to connect the first limit channel 31 and the second limit channel 32. The diameter D3 of the shaft body part of the crankshaft 10 located on the side of the second eccentric portion 12 away from the first eccentric portion 11, the diameter D4 of the center hole 34, and the diameter D2 of the second eccentric portion 12 satisfy: D3+2×e+2×L3＝D2, D2+2L5＝D4, wherein e is the eccentricity of the first eccentric portion 11, L3 is the third reserved gap between the outer surface of the shaft body part of the crankshaft 10 located on the side of the second eccentric portion 12 away from the first eccentric portion 11 and the outer surface at the proximal end of the second eccentric portion 12 (see Figure 5), and L5 is the fifth reserved gap between the second eccentric portion 12 and the hole wall of the center hole 34 when the second eccentric portion 12 is concentric with the center hole 34 (see Figure 4).

Preferably, the design range of the third reserved gap L3 is 0.05 mm to 3 mm.

Preferably, the design range of the fifth reserved gap L5 is 0.05 mm to 5 mm.

As shown in Fig. 8 and Fig. 9, the projection of the first slider 40 in the sliding direction is circular, and the projection of the second slider 70 in the sliding direction is square. In this way, the sliding reliability of the first slider 40 in the first limiting channel 31 and the sliding reliability of the second slider 70 in the second limiting channel 32 are ensured, and the processing convenience of the overall pump body assembly is ensured.

As shown in Figures 8 and 9, the width B1 of the second slider 70 and the diameter D5 of the first slider 40 satisfy: 0.5≤B1/D5≤1.5. In this way, by optimizing the size relationship between the width B1 of the second slider 70 and the diameter D5 of the first slider 40, it is ensured that the volume and mass of the second slider 70 and the first slider 40 are as close as possible, which is conducive to ensuring the dynamic balance of the compressor, thereby helping to reduce the noise of the compressor and ensure the reliability of the compressor. In addition, combined with the optimization of the gap between the first slider 40 and the first limiting channel 31, it is conducive to improving the energy efficiency of the compressor.

As shown in Fig. 8 and Fig. 9, the height H1 of the second slider 70 and the diameter D5 of the first slider 40 satisfy: 0.5≤H1/D5＜1. In this way, by optimizing the size relationship between the height H1 of the second slider 70 and the diameter D5 of the first slider 40, it is ensured that the volume and mass of the second slider 70 and the first slider 40 are as close as possible, which is conducive to ensuring the dynamic balance of the compressor, thereby helping to reduce the noise of the compressor and ensure the reliability of the compressor. In addition, combined with the optimization of the gap between the first slider 40 and the first limiting channel 31, it is conducive to improving the energy efficiency of the compressor.

It should be noted that, in the present application, there is a first reserved gap L1 between the outer peripheral surface of the first slider 40 and the channel wall of the first limiting channel 31, and the design range of the first reserved gap L1 is 0.008 mm to 0.05 mm. In this way, the first slider 40 can be properly assembled with the first limiting channel 31.

It should be noted that in the present application, in a direction perpendicular to the sliding direction of the second slider 70, there is a second reserved gap L2 between the outer surface of the second slider 70 and the channel wall of the second limiting channel 32, and the design range of the second reserved gap L2 is 0.008 mm to 0.05 mm. In this way, it is ensured that the second slider 70 can be normally assembled with the second limiting channel 32.

As shown in Fig. 6 to Fig. 9, the contour line of the first limiting channel 31 is matched with the outer contour line of the first slider 40, and the contour line of the second limiting channel 32 is matched with the outer contour line of the second slider 70. In this way, the sliding reliability of the first slider 40 in the first limiting channel 31 is ensured, and the sliding reliability of the second slider 70 in the second limiting channel 32 is ensured.

As shown in Fig. 7, the channel wall of the second limiting channel 32 has an arc transition angle R, and the angle range of the arc transition angle R is R ≥ 3 mm. In this way, the sealing reliability between the channel wall of the second limiting channel 32 and the second slider 70 is ensured.

As shown in FIG7 , the minimum sealing distance L between the first limiting channel 31 and the second limiting channel 32 satisfies: L≥2 mm. In this way, the sealing reliability of the cross groove structure 30 during the rotation process in the cylinder sleeve 20 is ensured.

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.

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

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.

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.

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.

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 "comprising" and/or "including" are used in this specification, it indicates the presence of features, steps, operations, devices, components and/or combinations thereof.

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.

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 (20)

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), and 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);

A first slider (40), the first slider (40) has a first through hole (41), the first eccentric portion (11) stretches into the first through hole (41), the first slider (40) is slidably arranged in the first limiting channel (31) and forms a first variable volume cavity (311), the first variable volume cavity (311) is located in the sliding direction of the first slider (40), and the crankshaft (10) rotates to drive the first slider (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 first slider (40) to rotate in the cylinder sleeve (20);

A second slider (70), the second slider (70) has a second through hole (71), the second eccentric portion (12) extends into the second through hole (71), the second slider (70) is slidably disposed in the second limiting channel (32) and forms a second variable volume cavity (321), the second variable volume cavity (321) is located in the sliding direction of the second slider (70), and the crankshaft (10) rotates to drive the second slider (70) to reciprocally slide in the second limiting channel (32) and interact with the cross groove structure (30) so as to enable the cross groove structure (30) and the second slider (70) to rotate in the cylinder sleeve (20);

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 one end of the cross groove structure (30) is in an open shape.

2. A fluid machine according to claim 1, characterized in that the fluid machine further comprises:

The upper flange (50) and the lower flange (60) are respectively arranged at two axial ends of the cylinder sleeve (20), and the end face of the second eccentric part (12) facing one side of the lower flange (60) is used as a thrust surface.

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 height of the first slider (40) in the axial direction of the cylinder liner (20) is greater than the height of the second slider (70) in the axial direction of the cylinder liner (20).

5. The fluid machine according to claim 1, characterized in that an opening (33) from which the crankshaft (10) protrudes is reserved in the end face of the end of the cross groove structure (30) that is not open, the opening (33) being arranged concentrically with the cross groove structure (30), the opening (33) being in communication with the first limiting channel (31).

6. The fluid machine according to claim 1, characterized in that the cross-slot structure (30) has a central hole (34), the central hole (34) being adapted to communicate between the first limiting channel (31) and the second limiting channel (32), the diameter D1 of the first eccentric portion (11), the diameter D2 of the second eccentric portion (12), the diameter D4 of the central hole (34) being such that: the design range of D4-D1 is 0.1-5 mm, and d1=d2.

7. 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 passage (31) and the second limiting passage (32), and a diameter D3 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), a diameter D4 of the center hole (34), and a diameter D2 of the second eccentric portion (12) satisfy: d3+2×e+2×l3=d2, d2+2l5=d4, wherein e is the eccentric amount of the first eccentric portion (11), L3 is a third reserved gap between the outer surface 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) and the outer surface at the proximal end of the second eccentric portion (12), and L5 is a fifth reserved gap between the second eccentric portion (12) and the hole wall surface of the center hole (34) when the second eccentric portion (12) is concentric with the center hole (34).

8. The fluid machine according to claim 7, wherein the third clearance L3 is designed to be in a range of 0.05mm to 3mm.

9. The fluid machine according to claim 7, wherein the fifth clearance L5 is designed in a range of 0.05mm to 5mm.

10. The fluid machine according to claim 1, wherein the projection of the first slider (40) in the sliding direction is circular and the projection of the second slider (70) in the sliding direction is square.

11. The fluid machine according to claim 10, wherein the width B1 of the second slider (70) and the diameter D5 of the first slider (40) satisfy: b1 is 0.5 ∈ D5 is less than or equal to 1.5.

12. The fluid machine according to claim 10, characterized in that between the height H1 of the second slider (70) and the diameter D5 of the first slider (40) is: H1/D5 is more than or equal to 0.5 and less than 1.

13. The fluid machine according to claim 10, wherein a first reserved gap L1 is provided between the outer peripheral surface of the first slider (40) and the channel wall of the first limiting channel (31), and the design range of the first reserved gap L1 is 0.008 mm-0.05 mm.

14. The fluid machine according to claim 10, wherein a second reserved gap L2 is provided between the outer surface of the second slider (70) and the channel wall of the second limiting channel (32) in a direction perpendicular to the sliding direction of the second slider (70), and the design range of the second reserved gap L2 is 0.008mm to 0.05mm.

15. The fluid machine according to claim 10, characterized in that the contour of the first limiting channel (31) is adapted to the outer contour of the first slider (40), and the contour of the second limiting channel (32) is adapted to the outer contour of the second slider (70).

16. The fluid machine according to claim 15, characterized in that the channel wall of the second limiting channel (32) has a circular arc transition angle R, and the angular range of the circular arc transition angle R is R > 3mm.

17. The fluid machine according to any one of claims 1 to 16, characterized in that a minimum sealing distance L between the first limiting channel (31) and the second limiting channel (32) is such that: l is more than or equal to 2mm.

18. The fluid machine according to any one of claims 1 to 16, 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.

19. The fluid machine according to claim 18, wherein the first eccentric portion (11) and the second eccentric portion (12) are arranged 180 ° opposite each other.

20. A heat exchange device comprising a fluid machine as claimed in any one of claims 1 to 19.