CN221568828U - Fluid machine and heat exchange device - Google Patents

Abstract

The utility model 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 height of the first sliding block in the axial direction of the cylinder sleeve is smaller than that of the second sliding block in the axial direction of the cylinder sleeve. The utility model solves the problems of lower energy efficiency and larger noise of the compressor in the prior art.

Description

Fluid machine and heat exchange device

Technical Field

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

Background

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

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

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

Disclosure of utility model

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

In order to achieve the above object, according to one aspect of the present utility model, there is provided a fluid machine including a crankshaft, a cylinder liner, a cross groove structure, a 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 first 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, an end surface of the first eccentric portion facing one side of the intersecting groove structure serves as a thrust surface so that the first eccentric portion is in thrust contact with the intersecting groove structure.

Further, the height of the first sliding block in the axial direction of the cylinder sleeve is smaller than the height of the second sliding block in the axial direction of the cylinder sleeve.

Further, the height of the first sliding block in the axial direction of the cylinder sleeve is smaller 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 second 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 D3 of the central hole meet the following conditions: d1 > D3 > 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 D4 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 D3 of the central hole and the diameter D2 of the second eccentric part satisfy the following conditions: d4+2×e+2×l1=d2, d2+2l5=d3, where e is the eccentric amount of the first eccentric portion, L1 is a first 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 first reserved gap L1 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 square, and the projection of the second sliding block in the sliding direction is circular.

Further, the width B1 of the first sliding block and the outer circle diameter D5 of the second sliding block satisfy the following conditions: b1 is 0.5 ∈ D5 is less than or equal to 1.5.

Further, the height H1 of the first sliding block in the axial direction of the cylinder sleeve and the outer circle diameter D5 of the second sliding block satisfy: H1/D5 is more than or equal to 0.5 and less than 1.

Further, in the direction perpendicular to the sliding direction of the first sliding block, a second reserved gap L2 is arranged between the outer surface of the first sliding block and the channel wall of the first limiting channel, and the design range of the second reserved gap L2 is 0.008 mm-0.05 mm.

Further, a third reserved gap L3 is arranged between the outer peripheral surface of the second sliding block and the channel wall of the second limiting channel, and the design range of the third reserved gap L3 is 0.008 mm-0.05 mm.

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

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

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

By adopting the technical scheme, the utility model provides a semi-closed double-cylinder four-compression structure, the cross groove structure is arranged into a structure form with the first limiting channel and the second limiting channel, the first sliding block is correspondingly arranged in the first limiting channel in a sliding way to form a first variable volume cavity, the first variable volume cavity is positioned in the sliding direction of the first sliding block, the crankshaft rotates to drive the first sliding block to slide reciprocally in the first limiting channel and interact with the cross groove structure so as to drive the cross groove structure and the first sliding block to rotate in the cylinder sleeve, in addition, the second sliding block is arranged in the second limiting channel in a sliding way to form a second variable volume cavity, and the crankshaft rotates to drive the second sliding block to slide reciprocally in the second limiting channel and interact with the cross groove structure so as to drive the cross groove structure and the second sliding block to rotate in the cylinder sleeve.

Further, the fluid machinery provided by the application can stably run, namely, the energy efficiency of the compressor is higher, the noise vibration is lower, the assembly is simple, the manufacturability of parts is good, and the like, so that the working reliability of the heat exchange equipment is ensured.

Drawings

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

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

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

FIG. 3 shows a schematic view of the crankshaft, cross slot configuration, and first slider block of the pump body assembly of FIG. 1 in an assembled state;

FIG. 4 shows a schematic view of the crankshaft, cross slot configuration, and other view of the first slider of FIG. 3;

FIG. 5 shows a schematic structural view of the pump body assembly of FIG. 1;

FIG. 6 shows an enlarged schematic view of the structure at C-C in FIG. 5;

FIG. 7 shows an enlarged schematic view of the structure at D-D in FIG. 5;

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

FIG. 9 shows a schematic structural view of the cross slot configuration of the pump body assembly of FIG. 2;

FIG. 10 is a schematic diagram showing the cross slot configuration of FIG. 4 from a top view of the crankshaft in an assembled state;

FIG. 11 shows a schematic structural view of a second slider of the pump body assembly of FIG. 2;

FIG. 12 shows a schematic structural view of the cross slot configuration of the pump body assembly of FIG. 2

FIG. 13 shows a schematic view of the first slider block of the pump body assembly of FIG. 2;

FIG. 14 shows a schematic structural view of another view of the cross slot configuration of the pump body assembly of FIG. 2;

FIG. 15 shows a noise contrast plot for a single cylinder dual compression compressor versus a semi-closed cross slot compressor at a noise condition of 0-1.2 kHz;

FIG. 16 shows a noise contrast plot for a single cylinder dual compression compressor versus a semi-closed cross slot compressor at a noise condition of 0-12.8 kHz;

FIG. 17 shows a graph comparing refrigeration capacities of a single cylinder dual compression structure compressor with a semi-closed cross-slot structure compressor under the same conditions;

FIG. 18 shows a graph of power consumption versus for a single cylinder dual compression compressor versus a semi-closed cross slot compressor under comparable conditions;

FIG. 19 shows a graph of performance versus performance for a single cylinder dual compression compressor versus a semi-closed cross-slot compressor under comparable conditions;

fig. 20 shows a schematic structural view of the shaft body portion and the second eccentric portion of the crankshaft in fig. 1 from a top view.

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. a second slider; 51. a second through hole;

60. An upper flange; 70. and a lower flange.

Detailed Description

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

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

As shown in fig. 1 to 19, the fluid machine includes a crankshaft 10, a cylinder liner 20, a cross groove structure 30, a first slider 40, and a second slider 50, wherein the crankshaft 10 is provided with a first eccentric portion 11 and a second eccentric portion 12 in the axial direction thereof; the crankshaft 10 and the cylinder sleeve 20 are eccentrically arranged and the eccentricity is fixed; the cross groove structure 30 is rotatably arranged in the cylinder sleeve 20, the cross groove structure 30 is provided with a first limiting channel 31 and a second limiting channel 32, the first limiting channel 31 and the second limiting channel 32 are sequentially arranged along the axial direction of the crankshaft 10, the first limiting channel 31 is positioned above the second limiting channel 32, 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 50 has a second through hole 51, the second eccentric portion 12 extends into the second through hole 51, the second slider 50 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 50, and the crankshaft 10 rotates to drive the second slider 50 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 50 rotate in the cylinder sleeve 20; the first limiting channel 31 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 application provides a 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 mode, 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 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 sliding block 40 rotate in a cylinder sleeve 20, in addition, a second sliding block 50 is arranged in the second limiting channel 32 in a sliding mode, a second variable volume cavity 321 is formed, the second sliding block 321 is positioned in the sliding direction of the second sliding block 50, and the crankshaft 10 rotates to drive the second sliding block 50 to slide back and forth in the second limiting channel 32 and interact with the cross groove structure 30, so that the cross groove structure 30 and the second sliding block 50 rotate in the cylinder sleeve 20 are avoided, the dead point position of a fluid machine is avoided, and the movement reliability of the fluid machine is improved, and the working reliability of heat exchange equipment is ensured.

Further, the fluid machinery provided by the application can stably run, namely, the energy efficiency of the compressor is higher, the noise vibration is lower, the assembly is simple, the manufacturability of parts is good, and the like, so that the working reliability of the heat exchange equipment is ensured.

It should be noted that the present application provides a novel double-cylinder four-compression semi-closed cross groove compressor, which not only can avoid the dead point problem of the compressor in principle based on the mechanism principle of the cross groove structure with two limiting channels and double sliding blocks, but also has the characteristics of high energy efficiency, simple assembly and good part manufacturability, and the following description specifically describes a compressor based on the cross groove structure 30 with the first limiting channel 31 and the second limiting channel 32, the first sliding block 40 and the second sliding block 50 by taking the compressor as an example.

As shown in fig. 1, the fluid machine further includes an upper flange 60 and a lower flange 70, and the upper flange 60 and the lower flange 70 are respectively disposed at both axial ends of the cylinder liner 20.

In the present application, the end surface of the first eccentric portion 11 facing the cross groove structure 30 serves as a thrust surface so that the first eccentric portion 11 is in thrust contact with the cross groove structure 30. In this way, the thrust surface of the present application is not carried by the upper flange 60, which is advantageous for reducing the abrasion of the end surface of the upper flange 60 and improving the reliability of the compressor.

In the present application, since the first limiting passage 31 penetrates the end surface of the intersecting groove structure 30 directly in the axial direction of the intersecting groove structure 30 so that one end of the intersecting groove structure 30 is open, the height of the first limiting passage 31 in the axial direction of the intersecting groove structure 30 is smaller than the height of the second limiting passage 32 in the axial direction of the intersecting groove structure 30, and as shown in fig. 1, 2 and 8, the height of the first eccentric portion 11 in the axial direction of the crankshaft 10 is smaller 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 smaller than the height of the second slider 50 in the axial direction of the cylinder liner 20. In this way, the fitting reliability when the first eccentric portion 11 is inserted into the first through hole 41 of the first slider 40 is ensured, and the fitting reliability when the second eccentric portion 12 is inserted into the second through hole 51 of the second slider 50 is ensured.

As shown in fig. 2 to 4, 12 and 14, 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 second limiting passage 32. In this way, the provision of the aperture 33 ensures that the shaft portion of the crankshaft 10 can pass through to ensure the assembly feasibility therebetween.

In the present application, in order to meet the assembly requirement of the pump body assembly of the compressor and the bearing surface of the crankshaft has a certain bearing area, as shown in fig. 8 and 9, 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 D3 of the central hole 34 satisfy: d1 > D3 > D2.

As shown in fig. 10, the cross groove structure 30 has a center hole 34, and the center hole 34 is used for communicating the first limiting passage 31 and the second limiting passage 32, and the diameter D4 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 D3 of the center hole 34, and the diameter D2 of the second eccentric portion 12 satisfy: d4+2×e+2×l1=d2, d2+2l5=d3, where e is the eccentric amount of the first eccentric portion 11, L1 is a first 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 wall surface of the center hole 34 when the second eccentric portion 12 is concentric with the center hole 34. In this way, the assembly feasibility of the pump body assembly is ensured.

Optionally, the design range of the first reserved gap L1 is 0.05 mm-3 mm. Thus, the assembly of the pump body assembly of the compressor is ensured to be simple and convenient.

Optionally, the design range of the fifth reserved gap L5 is 0.05 mm-5 mm.

As shown in fig. 11 and 13, the projection of the first slider 40 in the sliding direction thereof is square, and the projection of the second slider 50 in the sliding direction thereof is circular.

As shown in fig. 11 and 13, the width B1 of the first slider 40 and the outer diameter D5 of the second slider 50 satisfy: b1 is 0.5 ∈ D5 is less than or equal to 1.5. Therefore, the energy efficiency of the compressor is ensured not to be attenuated, the noise vibration of the compressor is reduced, and the reliability of the compressor is improved.

As shown in fig. 11 and 13, the height H1 of the first slider 40 in the axial direction of the cylinder liner 20 and the outer diameter D5 of the second slider 50 satisfy: H1/D5 is more than or equal to 0.5 and less than 1. Therefore, the energy efficiency of the compressor is ensured not to be attenuated, the noise vibration of the compressor is reduced, and the reliability of the compressor is improved.

In the present application, a second reserved gap L2 is formed between the outer surface of the first slider 40 and the channel wall of the first limiting channel 31 in a direction perpendicular to the sliding direction of the first slider 40, and the design range of the second reserved gap L2 is 0.008mm to 0.05mm. Thus, leakage and power consumption of the compressor are reduced, and energy efficiency of the compressor is improved.

In the present application, a third reserved gap L3 is provided between the outer peripheral surface of the second slider 50 and the channel wall of the second limiting channel 32, and the design range of the third reserved gap L3 is 0.008mm to 0.05mm. In this way, leakage between the second slider 50 and the cross slot structure 30 is advantageously reduced, thereby facilitating improved refrigeration capacity and performance of the compressor.

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

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

In the present application, the mass difference between the first eccentric part 11 and the second eccentric part 12 of the crankshaft 10, the limiting block and the piston of the single-cylinder double-compression compressor is larger, so that unbalanced centrifugal force between the upper cavity and the lower cavity is generated when the pump body operates, noise vibration of the compressor is affected, the mass difference between the upper and lower eccentric parts of the crankshaft of the semi-closed cross-shaped groove compressor and the upper and lower sliding blocks is smaller, the unbalanced centrifugal force between the upper and lower cavities is greatly reduced, and the noise vibration obtained by practical test has obvious advantages (see fig. 15 to 19).

As shown in fig. 15, the pump body assembly of the present application is abbreviated as a semi-closed cross groove, and compared with a noise curve of a pump body assembly of a single-cylinder double-compression structure in the prior art under the same condition, an abscissa in the graph is an operation frequency of a compressor, and an ordinate is a total noise value of the compressor, wherein a dotted line represents a curve of the pump body assembly of the single-cylinder double-compression structure, a solid line represents a curve of the pump body assembly of the semi-closed cross groove, and the total noise value range in the graph is 0-1.2 kHz.

As shown in fig. 16, the pump body assembly of the present application is abbreviated as a semi-closed cross groove, and compared with a noise curve of a pump body assembly of a single-cylinder double-compression structure in the prior art under the same condition, an abscissa in the graph is an operation frequency of a compressor, and an ordinate is a total noise value of the compressor, wherein a dotted line represents a curve of the pump body assembly of the single-cylinder double-compression structure, a solid line represents a curve of the pump body assembly of the semi-closed cross groove, and the total noise value range in the graph is 0-12.8 kHz.

As shown in fig. 17 to 19, the pump body assembly of the present application is abbreviated as a semi-closed cross groove, and compared with the curves of the cold capacity, the power consumption and the performance of the pump body assembly of the single-cylinder double-compression structure in the prior art, the horizontal axis in fig. 17 to 19 is the operating frequency of the pressure equalizing compressor, the vertical axis in fig. 17 is the refrigerating capacity of the compressor, the vertical axis in fig. 18 is the power consumption of the compressor, and the vertical axis in fig. 19 is the performance of the compressor, wherein the horizontal line represents the curve of the pump body assembly of the single-cylinder double-compression structure, the inclined line represents the curve of the pump body assembly of the semi-closed cross groove, and as can be clearly seen in fig. 17 to 19, the cold capacity and the performance of the semi-closed cross groove are higher than those of the pump body assembly of the single-cylinder double-compression structure under the same condition, and the power consumption of the semi-closed cross groove is reduced compared with the power consumption of the pump body assembly of the single-cylinder double-compression structure under the same condition.

In the application, the precision requirement of the double-cylinder four-compression compressor part is high, the process is complex, the leakage surface is more, the leakage amount of the compressor is large, the performance is unstable, the machining of the lower sliding block and the cross groove part of the semi-closed cross groove compressor is simple, the manufacturability is good, meanwhile, the tightness of the compressor is good, the leakage is less, and the actual test shows that the cold capacity of the compressor is increased, the power consumption is reduced, and the energy efficiency is improved.

In the application, the technical problems and beneficial effects are solved:

1. The dead point problem of the compressor in principle is avoided, leakage loss is reduced, and the efficiency of the compressor is improved;

2. The abrasion of the end face of the upper flange is reduced, and the reliability of the compressor is improved;

3. Parts of the pump body assembly are simplified, so that cost is saved, an assembly process is optimized, the manufacturability of the parts is good, and assembly and machining precision are guaranteed conveniently;

4. while taking into account energy efficiency, noise and vibration also have certain advantages.

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

The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present utility model unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters 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 on … …," "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 "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 exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.

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

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

Claims (17)

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);

The second sliding block (50) is provided with a second through hole (51), the second eccentric part (12) stretches into the second through hole (51), the second sliding block (50) is slidably arranged in the second limiting channel (32) and forms a second variable volume cavity (321), the second variable volume cavity (321) is positioned in the sliding direction of the second sliding block (50), and the crankshaft (10) rotates to drive the second sliding block (50) 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 sliding block (50) to rotate in the cylinder sleeve (20);

The first limiting channel (31) 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 according to claim 1, characterized in that an end face of the first eccentric portion (11) facing the side of the cross groove structure (30) serves as a thrust surface to bring the first eccentric portion (11) into thrust contact with the cross groove structure (30).

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 smaller 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 smaller than the height of the second slider (50) 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 second limiting channel (32).

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 D3 of the central hole (34) being such that: d1 > D3 > D2.

7. The fluid machine according to claim 1, characterized in that the cross groove structure (30) has a central hole (34), the central hole (34) being used for communicating the first limiting channel (31) and the second limiting channel (32), a diameter D4 of a shaft body portion of the crankshaft (10) located at a side of the second eccentric portion (12) remote from the first eccentric portion (11), a diameter D3 of the central hole (34), a diameter D2 of the second eccentric portion (12) being satisfied between: d4+2×e+2×l1=d2, d2+2l5=d3, where e is the eccentric amount of the first eccentric portion (11), L1 is a first 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 first clearance L1 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 its sliding direction is square and the projection of the second slider (50) in its sliding direction is circular.

11. The fluid machine according to claim 10, wherein the width B1 of the first slider (40) and the outer diameter D5 of the second slider (50) satisfy: b1 is 0.5 ∈ D5 is less than or equal to 1.5.

12. The fluid machine according to claim 10, wherein the height H1 of the first slider (40) in the axial direction of the cylinder liner (20), the outer diameter D5 of the second slider (50) satisfy: H1/D5 is more than or equal to 0.5 and less than 1.

13. The fluid machine according to claim 10, wherein a second reserved gap L2 is provided between the outer surface of the first slider (40) and the channel wall of the first limiting channel (31) in a direction perpendicular to the sliding direction of the first slider (40), and the design range of the second reserved gap L2 is 0.008mm to 0.05mm.

14. The fluid machine according to claim 10, wherein a third reserved gap L3 is provided between the outer peripheral surface of the second slider (50) and the channel wall of the second limiting channel (32), and the design range of the third reserved gap L3 is 0.008 mm-0.05 mm.

15. The fluid machine according to any one of claims 1 to 14, 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.

16. The fluid machine according to claim 15, wherein the first eccentric portion (11) and the second eccentric portion (12) are arranged 180 ° opposite each other.

17. A heat exchange device comprising a fluid machine as claimed in any one of claims 1 to 16.