CN117662467A - Fluid machine and heat exchange device - Google Patents

Abstract

The invention provides a fluid machine and heat exchange equipment, wherein the fluid machine comprises a crankshaft, a cylinder sleeve, a cross groove structure, a first sliding block and a second sliding block, wherein the crankshaft is provided with a first eccentric part and a second eccentric part; the crankshaft and the cylinder sleeve are eccentrically arranged, and the eccentric distance is fixed; the cross groove structure is rotatably arranged in the cylinder sleeve, and a first limit channel and a second limit channel of the cross groove structure are sequentially arranged along the axial direction of the crankshaft; the first eccentric part stretches into a first through hole of the first sliding block, and the first sliding block is arranged in the first limiting channel in a sliding manner and forms a first variable-volume cavity; the second eccentric part extends into a second through hole of the second sliding block, and the second sliding block is arranged in the second limiting channel in a sliding way and forms a second variable-volume cavity; 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. The invention solves the problem of low energy efficiency of the compressor in the prior art.

Description

Fluid machine and heat exchange device

Technical Field

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

Background

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

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

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

Disclosure of Invention

The invention mainly aims to provide a fluid machine and heat exchange equipment, which are used for solving the problem of low energy efficiency of a compressor in the prior art.

In order to achieve the above object, according to one aspect of the present invention, there is provided a fluid machine including a crankshaft, a cylinder liner, a cross groove structure, a first slider and a second slider, wherein the crankshaft is provided with a first eccentric portion and a second eccentric portion in an axial direction thereof; the crankshaft and the cylinder sleeve are eccentrically arranged, and the eccentric distance is fixed; the cross groove structure is rotatably arranged in the cylinder sleeve and is provided with a first limiting channel and a second limiting channel, the first limiting channel and the second limiting channel are sequentially arranged along the axial direction of the crankshaft, the first limiting channel is positioned above the second limiting channel, and the extending directions of the first limiting channel and the second limiting channel are perpendicular to the axial direction of the crankshaft; the first sliding block is provided with a first through hole, the first eccentric part extends into the first through hole, the first sliding block is arranged in the first limiting channel in a sliding way and forms a first variable-volume cavity, the first variable-volume cavity is positioned in the sliding direction of the first sliding block, and the crankshaft rotates to drive the first sliding block to slide back and forth in the first limiting channel and interact with the cross groove structure, so that the cross groove structure and the first sliding block rotate in the cylinder sleeve; the second sliding block is provided with a second through hole, the second eccentric part extends into the second through hole, the second sliding block is arranged in the second limiting channel in a sliding way and forms a second variable-volume cavity, the second variable-volume cavity is positioned in the sliding direction of the second sliding block, and the crankshaft rotates to drive the second sliding block to slide back and forth in the second limiting channel and interact with the cross groove structure at the same time so as to enable the cross groove structure and the second sliding block to rotate in the cylinder sleeve; 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.

Further, the fluid machine further comprises an upper flange and a lower flange, wherein the upper flange and the lower flange are respectively arranged at two axial ends of the cylinder sleeve, and the end face of the second eccentric part, which faces one side of the lower flange, is used as a thrust surface.

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 height of the first sliding block in the axial direction of the cylinder sleeve is larger than the height of the second sliding block in the axial direction of the cylinder sleeve.

Further, an opening for the crankshaft to extend is reserved on the end face of one end of the cross groove structure, which is not in an open shape, the opening and the cross groove structure are concentrically arranged, and the opening is communicated with the first limiting channel.

Further, the cross groove structure is provided with a central hole, the central hole is used for communicating a first limiting channel and a second limiting channel, and the diameter D1 of the first eccentric part, the diameter D2 of the second eccentric part and the diameter D4 of the central hole meet the following conditions: the design range of D4-D1 is 0.1-5 mm, and d1=d2.

Further, the cross groove structure is provided with a central hole, the central hole is used for communicating the first limiting channel and the second limiting channel, and the diameter D3 of the shaft body part of the crankshaft, which is positioned on one side of the second eccentric part far away from the first eccentric part, the diameter D4 of the central hole and the diameter D2 of the second eccentric part satisfy the following conditions: d3+2×e+2×l3=d2, d2+2l5=d4, where e is the eccentric amount of the first eccentric portion, L3 is a third reserved gap between the outer surface of the shaft body portion of the crankshaft 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 a fifth reserved gap between the second eccentric portion and the wall surface of the center hole when the second eccentric portion is concentric with the center hole.

Further, the design range of the third clearance L3 is 0.05 mm-3 mm.

Further, the design range of the fifth clearance L5 is 0.05 mm-5 mm.

Further, 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.

Further, the width B1 of the second slider and the diameter D5 of the first slider satisfy: B1/D5 is more than or equal to 0.5 and less than or equal to 1.5.

Further, the height H1 of the second slider and the diameter D5 of the first slider satisfy: H1/D5 is more than or equal to 0.5 and less than 1. Further, a first reserved gap L1 is arranged between the outer peripheral surface of the first sliding block and the channel wall of the first limiting channel, and the design range of the first reserved gap L1 is 0.008 mm-0.05 mm.

Further, in the direction perpendicular to the sliding direction of the second slider, a second reserved gap L2 is arranged 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-0.05 mm.

Further, the contour line of the first limiting channel is matched with the outer contour line of the first sliding block, and the contour line of the second limiting channel is matched with the outer contour line of the second sliding block.

Further, the arc transition angle R is arranged at the channel wall of the second limiting channel, and the angle range of the arc transition angle R is more than or equal to 3mm.

Further, the minimum sealing distance L between the first limiting channel and the second limiting channel satisfies: l is more than or equal to 2mm.

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

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

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

By adopting the technical scheme, the invention provides a semi-closed double-cylinder four-compression structure, and the cross groove structure is arranged in a structure form with a first limiting channel and a second limiting channel, a first sliding block is correspondingly arranged in the first limiting channel in a sliding way, a first variable volume cavity is formed, the first variable volume cavity is positioned in the sliding direction of the first sliding block, and a crankshaft rotates to drive the first 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 first sliding block rotate in a cylinder sleeve; in addition, the second sliding block is arranged in the second limiting channel in a sliding mode to form a second variable-volume cavity, the second variable-volume cavity is located in the sliding direction of the second sliding block, the crankshaft rotates to drive the second sliding block to slide back and forth in the second limiting channel and interact with the cross groove structure, so that the cross groove structure and the second sliding block rotate in the cylinder sleeve, 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.

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

Drawings

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

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

FIG. 2 shows an exploded view of the pump body assembly of FIG. 1;

FIG. 3 shows a schematic structural view of a crankshaft of the pump body assembly of FIG. 2;

FIG. 4 is a schematic diagram of the pump body assembly of FIG. 1 from a top view of the crankshaft, cross-slot configuration in an assembled condition;

FIG. 5 illustrates a schematic structural view of a shaft body portion and a second eccentric of the crankshaft of the pump body assembly of FIG. 1 from a top view;

FIG. 6 shows a schematic structural view of the cross slot configuration of the pump body assembly of FIG. 2;

FIG. 7 shows a schematic cross-sectional structural view of the cross-slot configuration of FIG. 5;

FIG. 8 shows a schematic structural view of a first slider of the pump body assembly of FIG. 2;

FIG. 9 shows a schematic structural view of a second slider of the pump body assembly of FIG. 2;

FIG. 10 shows a schematic view of the crankshaft, cross slot configuration, first slider, and second slider of the pump body assembly of FIG. 2 in an assembled state;

FIG. 11 shows a schematic cross-sectional view of the pump body assembly of FIG. 1 at a first slide;

fig. 12 shows a schematic cross-sectional view of the pump body assembly of fig. 1 at a second slide.

Wherein the above figures include the following reference numerals:

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

20. cylinder sleeve;

30. a cross slot structure; 31. a first limiting channel; 311. a first variable volume chamber; 32. the second limiting channel; 321. a second variable volume chamber; 33. opening holes; 34. a central bore;

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

50. an upper flange; 60. a lower flange;

70. a second slider; 71. and a second through hole.

Detailed Description

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

The existing rotary cylinder piston compressor is generally divided into two major types, namely a single cylinder rotary cylinder piston compressor and a double cylinder rotary cylinder piston compressor, wherein a cylinder of the single cylinder rotary cylinder piston compressor is designed in an axial closed mode (namely, a volume cavity is communicated with a radial direction and is in a completely closed state in the axial direction), the loss of gas leakage is small, the refrigerating capacity of the compressor is high, the compressor in the structural form still maintains the same design of a single eccentric part of a crankshaft as that of the single cylinder rotor compressor, namely, the torque peak value of the compressor is large, the vibration quantity of the compressor is large, the two ends of the cylinder of the double cylinder rotary cylinder piston compressor adopt an open design mode, the crankshaft is designed in a double eccentric part, the torque peak value of the compressor is greatly reduced, and the refrigerating capacity of the compressor is low due to the large gas leakage caused by the open structure.

In order to solve the problem of low energy efficiency of the compressor in the prior art, the invention provides a fluid machine and a heat exchange device, wherein the heat exchange device comprises the fluid machine, and the fluid machine is the fluid machine.

As shown in fig. 1 to 12, the fluid machine includes a crankshaft 10, a cylinder liner 20, a cross groove structure 30, a first slider 40 and a second slider 70, the crankshaft 10 being provided with a first eccentric portion 11 and a second eccentric portion 12 in an axial direction thereof; the crankshaft 10 and the cylinder sleeve 20 are eccentrically arranged and the eccentricity is fixed; the cross groove structure 30 is rotatably arranged in the cylinder sleeve 20, the cross groove structure 30 is provided with a first limiting channel 31 and a second limiting channel 32, the first limiting channel 31 and the second limiting channel 32 are sequentially arranged along the axial direction of the crankshaft 10, the first limiting channel 31 is positioned above the second limiting channel 32, 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; the first sliding block 40 is provided with a first through hole 41, the first eccentric part 11 extends into the first through hole 41, the first sliding block 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 positioned in the sliding direction of the first sliding block 40, and the crankshaft 10 rotates to drive the first sliding block 40 to reciprocally slide in the first limiting channel 31 and interact with the cross groove structure 30 at the same time so as to enable the cross groove structure 30 and the first sliding block 40 to 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 disposed in the second limiting channel 32 and forms a second volume-variable cavity 321, the second volume-variable 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 that the cross groove structure 30 and the second slider 70 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 open.

The application provides a semi-closed double-cylinder four-compression structure, which is characterized in that a cross groove structure 30 is provided with a first limiting channel 31 and a second limiting channel 32, a first sliding block 40 is correspondingly arranged in the first limiting channel 31 in a sliding way, a first variable volume cavity 311 is formed, the first variable volume cavity 311 is positioned in the sliding direction of the first sliding block 40, a crankshaft 10 rotates to drive the first 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 first sliding block 40 rotate in a cylinder sleeve 20; in addition, 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 that the cross groove structure 30 and the second slider 70 rotate in the cylinder sleeve 20, and as a result, dead point positions of the fluid machinery are avoided, movement reliability of the fluid machinery is improved, and working reliability of the heat exchange device is ensured.

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

It should be noted that, in the present application, the first slider 40 is slidably disposed in the first limiting channel 31 and forms the first variable volume chambers 311, and the first variable volume chambers 311 are located in the sliding direction of the first slider 40, and since the first slider 40 slides reciprocally in the first limiting channel 31, the first variable volume chambers 311 are two; similarly, there are two second variable volume chambers 321 (see fig. 10 to 11).

This application is through setting up the one end of crossing groove structure 30 to be the structural style of uncovered form for first spacing passageway 31 and second spacing passageway 32 have realized the differentiation design, and promptly, the one end of crossing groove structure 30 is uncovered, and the other end of crossing groove structure 30 is sealed, ensures the inside seal reliability of the pump body subassembly of compressor, thereby reaches the purpose that reduces the torque peak value of compressor, and then is favorable to promoting the performance of compressor.

As shown in fig. 1 and 2, the fluid machine further includes an upper flange 50 and a lower flange 60, the upper flange 50 and the lower flange 60 being disposed at axial ends of the cylinder liner 20, respectively, and an end surface of the second eccentric portion 12 facing the lower flange 60 side being a thrust surface. In this way, it is ensured that the end surface of the second eccentric portion 12 facing the lower flange 60 is used as a thrust surface, thereby supporting the entire rotary shaft.

In this application, considering that the second limiting passage 32 directly penetrates the end face of the cross groove structure 30 along the axial direction of the cross groove structure 30, so that the end of the cross groove structure 30 having the second limiting passage 32 is open, the height of the first limiting passage 31 in the axial direction of the cross groove structure 30 is set higher than the height of the second limiting passage 32 in the axial direction of the cross groove structure 30, so as to prevent leakage, as shown in fig. 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 liner 20 is greater than the height of the second slider 70 in the axial direction of the cylinder liner 20. In this way, the suitability of the first eccentric portion 11 to be inserted into the first through hole 41 when the first slider 40 is slidably disposed in the first limiting passage 31 is ensured, and the suitability of the second eccentric portion 12 to be inserted into the second through hole 71 when the second slider 70 is slidably disposed in the second limiting passage 32 is ensured.

As shown in fig. 7, an opening 33 through which the crankshaft 10 extends is reserved in the end face of the end of the cross groove structure 30 that is not open, the opening 33 being disposed concentrically with the cross groove structure 30, the opening 33 being in communication with the first limiting passage 31. In this way, the assembling feasibility between the crankshaft 10 and the cross groove structure 30 is ensured.

In this application, in order to ensure that the crankshaft 10 and the cross groove structure 30 can be assembled normally and reduce leakage between the axial gaps, as shown in fig. 7, the cross groove structure 30 has a central hole 34, the central hole 34 is used for communicating the first limiting channel 31 and the second limiting channel 32, and the diameter D1 of the first eccentric portion 11, the diameter D2 of the second eccentric portion 12, and the diameter D4 of the central hole 34 satisfy: the design range of D4-D1 is 0.1-5 mm, and d1=d2.

In this application, in order to ensure the assembly feasibility between the crankshaft 10 and the cross groove structure 30, further, the cross groove structure 30 has a center hole 34, the center hole 34 is used to communicate the first limiting passage 31 and the second limiting passage 32, and the diameter D3 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, 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, where e is the eccentric amount of the first eccentric portion 11, L3 is a third reserved gap (see fig. 5) 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 (see fig. 4) between the second eccentric portion 12 and the wall surface of the center hole 34 when the second eccentric portion 12 is concentric with the center hole 34.

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

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

As shown in fig. 8 and 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 passage 31 is ensured, and the processing convenience of the whole pump body assembly is ensured while the sliding reliability of the second slider 70 in the second limiting passage 32 is ensured.

As shown in fig. 8 and 9, the width B1 of the second slider 70 and the diameter D5 of the first slider 40 satisfy: B1/D5 is more than or equal to 0.5 and less than or equal to 1.5. In this way, by optimizing the dimension relationship between the width B1 of the second slider 70 and the diameter D5 of the first slider 40, the volume and the mass between the second slider 70 and the first slider 40 are ensured to be as close as possible, so that dynamic balance of the compressor is ensured, noise of the compressor is reduced, reliability of the compressor is ensured, and in addition, energy efficiency of the compressor is improved by combining the optimization of the gap between the first slider 40 and the first limiting channel 31.

As shown in fig. 8 and 9, the height H1 of the second slider 70 and the diameter D5 of the first slider 40 satisfy: H1/D5 is more than or equal to 0.5 and less than 1. In this way, by optimizing the range of the dimensional 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 the mass between the second slider 70 and the first slider 40 are as close as possible, so that it is advantageous to ensure dynamic balance of the compressor, further to reduce noise of the compressor, and simultaneously to ensure reliability of the compressor, and in addition, it is advantageous to improve energy efficiency of the compressor by combining the optimization of the gap between the first slider 40 and the first limiting channel 31.

In the present application, 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 0.008mm to 0.05mm. In this way, it is ensured that the first slider 40 can be normally assembled with the first limiting passage 31.

In the present application, a second reserved gap L2 is formed 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. In this way, it is ensured that the second slider 70 can be normally assembled with the second limiting passage 32.

As shown in fig. 6 to 9, 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. In this way, the sliding reliability of the first slider 40 in the first limiting passage 31 is ensured, and the sliding reliability of the second slider 70 in the second limiting passage 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.gtoreq.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 fig. 7, the minimum sealing distance L between the first limiting passage 31 and the second limiting passage 32 satisfies: l is more than or equal to 2mm. In this way, the seal reliability of the cross groove structure 30 during rotation of the cylinder liner 20 is ensured.

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

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

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

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

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

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

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

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

Claims (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. The fluid machine of claim 1, further comprising:

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/D5 is more than or equal to 0.5 and 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.