CN116292303A

CN116292303A - Fluid machine and heat exchange device with bearing

Info

Publication number: CN116292303A
Application number: CN202111487187.9A
Authority: CN
Inventors: 杜忠诚; 张培林; 任丽萍; 李直; 宋雪威; 于瑞波
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2021-12-07
Filing date: 2021-12-07
Publication date: 2023-06-23

Abstract

The invention provides a fluid machine with a bearing and heat exchange equipment, wherein the fluid machine comprises a crankshaft, a cylinder sleeve, a bearing, a cross groove structure and a sliding block, and the crankshaft is provided with two eccentric parts; the crankshaft and the cylinder sleeve are eccentrically arranged, and the eccentric distance is fixed; the bearing is arranged in the cylinder sleeve, and the outer ring of the bearing is attached to the inner wall of the cylinder sleeve; the crossed groove structure is rotatably arranged in the cylinder sleeve, the outer peripheral surface of the crossed groove structure is attached to the inner ring of the bearing, the ratio between the height H1 of the bearing and the height H2 of the cylinder sleeve is more than 0.9 and less than 1, two limiting channels of the crossed groove structure are sequentially arranged along the axial direction of the crankshaft, and the extending direction of the limiting channels is perpendicular to the axial direction of the crankshaft; the sliding blocks are provided with through holes, the two eccentric parts correspondingly extend into the two through holes of the two sliding blocks, and the two sliding blocks are correspondingly arranged in the two limiting channels in a sliding manner and form a variable-volume cavity. The invention solves the problems of lower energy efficiency and larger noise of the compressor in the prior art.

Description

Fluid machine and heat exchange device with bearing

Technical Field

The invention relates to the technical field of heat exchange systems, in particular to a fluid machine with a bearing 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 with a bearing and heat exchange equipment, so as to solve 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 invention, there is provided a fluid machine having a bearing, including a crankshaft, a cylinder liner, a bearing, a cross groove structure, and a slider, wherein the crankshaft is provided with two eccentric portions in an axial direction thereof; the crankshaft and the cylinder sleeve are eccentrically arranged, and the eccentric distance is fixed; the bearing is arranged in the cylinder sleeve, and the outer ring of the bearing is attached to the inner wall of the cylinder sleeve; the crossed groove structure is rotatably arranged in the cylinder sleeve, the outer peripheral surface of the crossed groove structure is attached to the inner ring of the bearing, the ratio between the height H1 of the bearing and the height H2 of the cylinder sleeve is more than 0.9 and less than 1, the crossed groove structure is provided with two limiting channels, the two limiting channels are sequentially arranged along the axial direction of the crankshaft, and the extending direction of the limiting channels is perpendicular to the axial direction of the crankshaft; the sliding block is provided with two through holes, the two eccentric parts correspondingly extend into the two through holes of the two sliding blocks, the two sliding blocks are correspondingly arranged in the two limiting channels in a sliding mode and form a variable-volume cavity, the variable-volume cavity is located in the sliding direction of the sliding block, and the crankshaft rotates to drive the sliding block to slide back and forth in the limiting channels and interact with the cross groove structure, so that the cross groove structure and the sliding block rotate in the cylinder sleeve.

Further, the height H1 of the bearing and the height H2 of the cylinder sleeve satisfy the following conditions: H2-H1 is more than or equal to 0.003mm and less than or equal to 0.1mm.

Further, a phase difference of a first included angle A is formed between the two eccentric parts, the eccentric amounts of the two eccentric parts are equal, and a phase difference of a second included angle B is formed between the extending directions of the two limiting channels, wherein the first included angle A is twice the second included angle B.

Further, the eccentric amount of the eccentric portion is equal to the fitting eccentric amount of the crankshaft and the cylinder liner.

Further, both ends of the limiting channel are communicated to the outer peripheral surface of the cross groove structure.

Further, the two sliding blocks are respectively arranged concentrically with the two eccentric parts, the sliding blocks do circular motion around the eccentric parts, a first rotating gap is arranged between the hole wall of the through hole and the eccentric parts, and the range of the first rotating gap is 0.005-0.05 mm.

Further, the periphery of the cylinder sleeve is provided with a circumferential convex ring, and a plurality of strip holes which are arranged at intervals are formed in the circumferential convex ring.

Further, the first included angle A is 160-200 degrees; the second included angle B is 80-100 degrees.

Further, the fluid machine further comprises a flange, the flange is arranged at the axial end part of the cylinder sleeve, and the crankshaft and the flange are arranged concentrically.

Further, a first assembly gap is arranged between the crankshaft and the flange, and the range of the first assembly gap is 0.005 mm-0.05 mm.

Further, the first fitting clearance is in the range of 0.01 to 0.03mm.

Further, the eccentric portion has an arc surface, and a central angle of the arc surface is 180 degrees or more.

Further, the eccentric portion is cylindrical.

Further, the proximal end of the eccentric portion is flush with the outer circumference of the shaft body portion of the crankshaft; or, the proximal end of the eccentric part protrudes out of the outer circle of the shaft body part of the crankshaft; alternatively, the proximal end of the eccentric portion is located inside the outer circumference of the shaft body portion of the crankshaft.

Further, the sliding block comprises a plurality of substructures, and the substructures are spliced to form a through hole.

Further, the two eccentric portions are provided at intervals in the axial direction of the crankshaft.

Further, the cross groove structure is provided with a central hole, the two limiting channels are communicated through the central hole, and the aperture of the central hole is larger than the diameter of the shaft body part of the crankshaft.

Further, the bore diameter of the central bore is larger than the diameter of the eccentric portion.

Further, the projection of the slider in the axial direction of the through hole is provided with two relatively parallel straight line segments and an arc line segment connecting the ends of the two straight line segments.

Further, the slider has a pressing surface facing the end of the limiting passage, the pressing surface being a head of the slider, the pressing surface facing the variable volume chamber.

Further, the extrusion surface is an arc surface, and the distance between the arc center of the arc surface and the center of the through hole is equal to the eccentric amount of the eccentric part.

Further, the radius of curvature of the cambered surface is equal to the radius of the inner circle of the cylinder sleeve; or the radius of curvature of the cambered surface and the radius of the inner circle of the cylinder sleeve have a difference value, and the range of the difference value is-0.05 mm to 0.025mm.

Further, the difference ranges from-0.02 to 0.02mm.

Further, a projected area S of the pressing surface in the sliding direction of the slider _{Sliding block} The area of the compression exhaust port with the cylinder sleeve is S _{Row of rows} The following are satisfied: s is S _{Sliding block} /S _{Row of rows} The value of (2) is 8 to 25.

Further, S _{Sliding block} /S _{Row of rows} The value of (2) is 12 to 18.

Further, the fluid machinery comprises two flanges which are respectively assembled at two axial ends of the cylinder sleeve, the two flanges are respectively provided with an air inlet channel, the two air inlet channels are respectively communicated with the two limiting channels, the two flanges are respectively provided with an air outlet channel, and a phase difference exists between the air inlet channel and the air outlet channel on the same flange.

Further, the air inlet channel comprises a first air inlet channel section and a second air inlet channel section which are communicated in sequence, the first air inlet channel section extends along the radial direction of the flange, and the second air inlet channel section extends along the axial direction of the flange.

Further, an exhaust groove is formed in the end face of one side, away from the cylinder sleeve, of the flange, an exhaust communication opening is formed in the bottom of the exhaust groove and is communicated with the limiting channel, and the exhaust communication opening extends along the axial direction of the flange.

Further, the tail end of the air inlet channel is an air inlet communication port, the initial end of the air outlet channel is an air outlet communication port, and when any sliding block is positioned at the air inlet position, the air inlet communication port is communicated with the corresponding volume cavity; when any slide block is at the exhaust position, the corresponding volume cavity is communicated with the exhaust communication port.

Further, the fluid machine is a compressor.

Further, the tail end of the air inlet channel is an air inlet communication port, the initial end of the air outlet channel is an air outlet communication port, and when any sliding block is positioned at the air inlet position, the air outlet communication port is communicated with the corresponding volume cavity; when any slide block is at the exhaust position, the corresponding volume cavity is communicated with the air inlet communication port.

Further, the fluid machine is an expander.

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 cross groove structure is provided with the structure form with the two limiting channels, the two eccentric parts of the crankshaft correspondingly extend into the two through holes of the two sliding blocks, and the two sliding blocks correspondingly slide in the two limiting channels to form the variable volume cavity, so that when one of the two sliding blocks is at the dead point position, namely, the driving torque of the eccentric part corresponding to the sliding block at the dead point position is 0, the sliding block at the dead point position cannot continuously rotate, and at the moment, the driving torque of the other eccentric part of the two eccentric parts drives the corresponding sliding block to be the maximum value, so that the eccentric part with the maximum driving torque can normally drive the corresponding sliding block to rotate, the cross groove structure is driven to rotate through the sliding block, the sliding block at the dead point position is driven to continuously rotate through the cross groove structure, the stable operation of the fluid machine is realized, the dead point position of the moving mechanism is avoided, the moving reliability of the fluid machine is improved, and the working reliability of the heat exchange equipment is ensured.

In addition, through setting up the bearing in the cylinder liner and the outer lane of bearing is laminated with the inner wall of cylinder liner, it is more than 0.9 and less than 1 to prescribe a limit to the ratio between the height H1 of bearing and the height H2 of cylinder liner simultaneously, like this, the whole excircle in the axial of cross groove structure is through bearing support antifriction for change the rolling friction of circumference external surface and the bearing of cross groove structure from sliding friction between the circumference external surface of cross groove structure and the inner wall of cylinder liner, mechanical friction consumption has been reduced, wherein, the inner circle and the cross groove structure cooperation of bearing, the inner circle and the inner wall cooperation of cylinder liner of bearing.

Further, as the fluid machinery provided by the application can stably run, namely, the energy efficiency of the compressor is ensured to be higher, the noise is smaller, and therefore 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 illustrates a schematic mechanical diagram of the operation of a compressor in accordance with an alternative embodiment of the present invention;

FIG. 2 is a schematic diagram showing the principle of the mechanism of operation of the compressor of FIG. 1;

FIG. 3 is a schematic view showing an internal structure of a compressor according to an alternative embodiment of the present invention;

FIG. 4 shows a schematic structural view of a pump body assembly of the compressor of FIG. 3;

FIG. 5 shows an exploded view of the pump body assembly of FIG. 4;

FIG. 6 shows a schematic diagram of a comparison of the height H1 of the bearing and the height H2 of the cylinder liner in FIG. 5;

FIG. 7 is a schematic view showing the crankshaft, cross slot structure, and slider of FIG. 5 in an assembled state;

FIG. 8 shows a schematic cross-sectional view of the crankshaft, cross slot configuration, and slider of FIG. 7;

FIG. 9 is a schematic view showing the structure of the shaft body portion and the eccentric amounts of the two eccentric portions of the crankshaft in FIG. 5;

FIG. 10 is a schematic cross-sectional structural view showing the amount of assembly eccentricity of the crankshaft and cylinder liner of FIG. 5;

FIG. 11 shows a schematic view of the cylinder liner and lower flange of FIG. 5 in an exploded condition;

FIG. 12 is a schematic view showing the structure of the eccentricity between the cylinder liner and the lower flange of FIG. 11;

FIG. 13 shows a schematic view of the slider of FIG. 5 in the axial direction of the through hole;

fig. 14 shows a schematic structural view of the intake passage and the exhaust passage of the upper flange in fig. 5;

fig. 15 shows a schematic structural view of an intake passage and an exhaust passage of the lower flange of fig. 5;

FIG. 16 shows a schematic view of the upper flange and cylinder liner of FIG. 14 in an assembled condition;

FIG. 17 is a schematic diagram showing the structure of the I-I view of FIG. 16;

FIG. 18 is a schematic view showing the structure of view II-II in FIG. 17, in which the compressor is in a suction state;

FIG. 19 is a schematic view showing the structure of view II-II in FIG. 17, in which the compressor is in a compressed gas state;

FIG. 20 is a schematic view showing the structure of view II-II in FIG. 17, in which the compressor is in a discharge state;

FIG. 21 shows an exploded view of the pump body assembly of FIG. 4 with bearings;

FIG. 22 shows a schematic diagram of a cross slot configuration and slider configuration in accordance with an alternative embodiment of the present invention;

FIG. 23 shows a schematic diagram of a cross slot configuration and slider configuration in accordance with an alternative embodiment of the present invention;

FIG. 24 shows a schematic view of a cross slot configuration and slider configuration in accordance with an alternative embodiment of the present invention;

FIG. 25 shows a schematic view of a cross slot configuration and slider configuration in accordance with an alternative embodiment of the present invention;

FIG. 26 is a schematic diagram showing the principle of the prior art compressor operation;

FIG. 27 is a schematic diagram of the mechanism of operation of the compressor modified in the prior art;

FIG. 28 is a schematic view of the mechanism of operation of the compressor of FIG. 27 showing the moment arm of the drive shaft driving the slider in rotation;

fig. 29 shows a schematic view of the principle of the mechanism of operation of the compressor of fig. 27, in which the center of the limit groove structure and the center of the eccentric portion coincide.

Wherein the above figures include the following reference numerals:

10. a crankshaft; 11. a eccentric portion; 12. a shaft body portion;

20. cylinder sleeve; 28. a circumferential collar; 281. a slit hole;

30. a cross slot structure; 31. a limiting channel; 311. a variable volume chamber; 32. a central bore;

40. a slide block; 41. a through hole; 42. extruding the surface;

50. a flange; 51. an exhaust passage; 52. an upper flange; 53. a lower flange; 54. an air intake passage; 541. a first intake passage section; 542. a second intake passage section; 55. an exhaust groove; 551. an exhaust communication port;

80. a knockout component; 81. a housing assembly; 82. a motor assembly; 83. a pump body assembly; 84. an upper cover assembly; 85. a lower cover assembly;

90. a fastener;

200. and (3) a bearing.

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.

In the prior art, as shown in FIG. 26, a compressor operating mechanism principle is proposed based on a crosshead shoe mechanism, i.e., at point O ₁ As cylinder center, point O ₂ As the center of the driving shaft, point O ₃ As the center of the slide block, the cylinder is eccentrically arranged with the driving shaft, wherein the center O of the slide block ₃ At a diameter of O ₁ O ₂ Is moved circularly on a circle.

In the operating mechanism principle, the cylinder center O ₁ And drive shaft center O ₂ As two rotation centers of the movement mechanism, simultaneously, line segment O ₁ O ₂ Is the midpoint O of (1) ₀ As the center O of the slide block ₃ So that the slide is reciprocated relative to the cylinder and also to the drive shaft.

Due to line segment O ₁ O ₂ Is the midpoint O of (1) ₀ As a virtual center, a problem of deterioration of high-frequency vibration characteristics of a compressor due to failure to provide a balance system, based on the principle of the above-described operation mechanism, as shown in fig. 27, a method of using O ₀ As a movement mechanism of the drive shaft center, i.e. cylinder center O ₁ And drive shaft center O ₀ As two rotation centers of the motion mechanism, the driving shaft is provided with an eccentric part, the sliding block is coaxially arranged with the eccentric part, and the assembly eccentric amount of the driving shaft and the cylinder is equal to the eccentric amount of the eccentric part, so that the sliding block is provided with a center O ₃ About the drive axis center O ₀ Is used as the center of a circle and takes O as ₁ O ₀ Circular motion is performed for the radius.

Correspondingly, a set of running mechanism is providedThe device comprises a cylinder, a limit groove structure, a sliding block and a driving shaft, wherein the limit groove structure is rotatably arranged in the cylinder, and the cylinder and the limit groove structure are coaxially arranged, namely, the center O of the cylinder ₁ The sliding block is assembled coaxially with the eccentric part of the driving shaft, the sliding block performs circular motion around the shaft body part of the driving shaft, and the specific motion process is as follows: the driving shaft rotates to drive the sliding block to revolve around the center of the shaft body part of the driving shaft, the sliding block rotates relative to the eccentric part at the same time, and the sliding block reciprocates in the limiting groove of the limiting groove structure and pushes the limiting groove structure to rotate.

However, as shown in fig. 28, the length of the arm L of force for driving the rotation of the slider is l=2e×cos θ×cos θ, where e is the eccentric amount of the eccentric portion, and θ is O ₁ O ₀ And an included angle between the connecting line and the sliding direction of the sliding block in the limiting groove.

As shown in FIG. 29, when the cylinder is centered at O ₁ When the center of the limit groove structure and the center of the eccentric portion are coincident, the resultant force of the driving shaft passes through the center of the limit groove structure, that is, the torque applied to the limit groove structure is zero, the limit groove structure cannot rotate, and the movement mechanism is at the dead point position and cannot drive the sliding block to rotate.

Based on this, this application has provided a brand-new mechanism principle that possesses two spacing passageway's cross groove structure and two sliders to construct a brand-new compressor based on this principle, this compressor possesses the characteristics that energy efficiency is high, the noise is little, takes the compressor as the example below, specifically introduces the compressor based on possessing two spacing passageway's cross groove structure and two sliders.

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

The fluid machine with the bearing in the present invention comprises a crankshaft 10, a cylinder liner 20, a bearing 200, a cross groove structure 30 and a slider 40, wherein the crankshaft 10 is provided with two eccentric parts 11 along the axial direction thereof; the crankshaft 10 and the cylinder sleeve 20 are eccentrically arranged, and the eccentric distance is fixed; the bearing 200 is arranged in the cylinder sleeve 20, and the outer ring of the bearing 200 is attached to the inner wall of the cylinder sleeve 20; the cross groove structure 30 is rotatably arranged in the cylinder sleeve 20, the outer peripheral surface of the cross groove structure 30 is attached to the inner ring of the bearing 200, the ratio between the height H1 of the bearing 200 and the height H2 of the cylinder sleeve 20 is more than 0.9 and less than 1, the cross groove structure 30 is provided with two limiting channels 31, the two limiting channels 31 are sequentially arranged along the axial direction of the crankshaft 10, and the extending direction of the limiting channels 31 is perpendicular to the axial direction of the crankshaft 10; the sliding blocks 40 are provided with through holes 41, the two eccentric parts 11 correspondingly extend into the two through holes 41 of the two sliding blocks 40, the two sliding blocks 40 are correspondingly arranged in the two limiting channels 31 in a sliding mode and form a variable-volume cavity 311, the variable-volume cavity 311 is positioned in the sliding direction of the sliding blocks 40, the crankshaft 10 rotates to drive the sliding blocks 40 to slide back and forth in the limiting channels 31 and interact with the cross groove structure 30, and the cross groove structure 30 and the sliding blocks 40 rotate in the cylinder sleeve 20.

By arranging the cross groove structure 30 in a structure form with two limiting channels 31 and correspondingly arranging two sliding blocks 40, two eccentric parts 11 of a crankshaft correspondingly extend into two through holes 41 of the two sliding blocks 40, and simultaneously, the two sliding blocks 40 correspondingly slide in the two limiting channels 31 and form a variable-volume cavity 311, when one of the two sliding blocks 40 is at a dead point position, namely, the driving torque of the eccentric part 11 corresponding to the sliding block 40 at the dead point position is 0, the sliding block 40 at the dead point position cannot continuously rotate, at the moment, the driving torque of the other eccentric part 11 of the two eccentric parts 11 drives the corresponding sliding block 40 to be the maximum value, so that the eccentric part 11 with the maximum driving torque can normally drive the corresponding sliding block 40 to rotate, the cross groove structure 30 is driven to rotate through the sliding block 40, the sliding block 40 at the dead point position is driven to continuously rotate through the cross groove structure 30, the dead point position of a fluid machine is avoided, the reliability of the movement of the fluid machine is improved, and the working reliability of the heat exchange equipment is ensured.

In addition, by disposing the bearing 200 inside the cylinder liner 20 with the outer ring of the bearing 200 fitted to the inner wall of the cylinder liner 20 while defining a ratio between the height H1 of the bearing 200 and the height H2 of the cylinder liner 20 greater than 0.9 and less than 1, the entire outer circumference in the axial direction of the intersecting groove structure 30 is antifriction supported by the bearing 200 such that sliding friction between the circumferential outer surface of the intersecting groove structure 30 and the inner wall of the cylinder liner 20 is changed into rolling friction between the circumferential outer surface of the intersecting groove structure 30 and the bearing 200, wherein the inner ring of the bearing 200 is fitted to the intersecting groove structure 30 and the inner ring of the bearing 200 is fitted to the inner wall of the cylinder liner 20, mechanical friction power consumption is reduced.

It should be noted that, in the present application, both the first included angle a and the second included angle B are not zero.

As shown in fig. 1 and 2, when the fluid machine described above is operated, the crankshaft 10 is wound around the axis O of the crankshaft 10 ₀ Autorotation; the cross groove structure 30 is formed around the axial center O of the crankshaft 10 ₀ Revolution, the axis O of the crankshaft 10 ₀ With the axis O of the cross slot structure 30 ₁ The eccentric arrangement is carried out with fixed eccentric distance; the first slide block 40 is arranged at the axis O of the crankshaft 10 ₀ The center O of the first slide 40 moves circularly ₃ With the axis O of the crankshaft 10 ₀ The distance between the two eccentric parts is equal to the eccentric amount of the first eccentric part 11 corresponding to the crankshaft 10, and the eccentric amount is equal to the axis O of the crankshaft 10 ₀ With the axis O of the cross slot structure 30 ₁ The eccentric distance between the two sliding blocks, the crankshaft 10 rotates to drive the first sliding block 40 to do circular motion, and the first sliding block 40 interacts with the cross groove structure 30 and slides reciprocally in the limiting channel 31 of the cross groove structure 30; the second slide block 40 is arranged at the axis O of the crankshaft 10 ₀ A center O of the second slide 40 moves circularly for the center of the circle ₄ With the axis O of the crankshaft 10 ₀ The distance between the two eccentric parts is equal to the eccentric amount of the second eccentric part 11 corresponding to the crankshaft 10, and the eccentric amount is equal to the axis O of the crankshaft 10 ₀ With the axis O of the cross slot structure 30 ₁ Eccentric distance between them, the crankshaft 10 rotates to drive the second slide 40 to do circular motion, and the second slide 40 interacts with and intersects the cross slot structure 30The fork groove structure 30 slides reciprocally in the limit channel 31.

The fluid machine operating as described above constitutes a slider-cross mechanism, which employs the slider-cross mechanism principle, wherein the two eccentric portions 11 of the crankshaft 10 are each provided as a first connecting rod L ₁ And a second connecting rod L ₂ The two limiting channels 31 of the cross slot structure 30 are respectively used as the third connecting rod L ₃ And a fourth connecting rod L ₄ And a first link L ₁ And a second connecting rod L ₂ Is equal (please refer to fig. 1).

As shown in FIG. 1, a first link L ₁ And a second connecting rod L ₂ A first included angle A and a third connecting rod L are arranged between ₃ And a fourth connecting rod L ₄ The first included angle A is twice as large as the second included angle B.

As shown in fig. 2, the axis O of the crankshaft 10 ₀ With the axis O of the cross slot structure 30 ₁ The connection line between the two is connection line O ₀ O ₁ First connecting rod L ₁ And connecting line O ₀ O ₁ A third included angle C is formed between the two connecting rods, and a corresponding third connecting rod L ₃ And connecting line O ₀ O ₁ A fourth included angle D is formed between the first and second inclined angles, wherein the third included angle C is twice the fourth included angle D; second connecting rod L ₂ And connecting line O ₀ O ₁ A fifth included angle E is formed between the two connecting rods, and a corresponding fourth connecting rod L ₄ And connecting line O ₀ O ₁ A sixth included angle F is formed between the two surfaces, wherein the fifth included angle E is twice as large as the sixth included angle F; the sum of the third included angle C and the fifth included angle E is a first included angle A, and the sum of the fourth included angle D and the sixth included angle F is a second included angle B.

Further, the operation method further comprises the rotation angular velocity of the sliding block 40 relative to the eccentric part 11 and the rotation angular velocity of the sliding block 40 around the axis O of the crankshaft 10 ₀ The revolution angular velocity of (2) is the same; the cross groove structure 30 is formed around the axial center O of the crankshaft 10 ₀ The revolution angular velocity of the slider 40 is the same as the rotation angular velocity of the eccentric portion 11.

Specifically, the axis O of the crankshaft 10 ₀ Equivalent to the first connecting rod L ₁ And a second connecting rod L ₂ The center of rotation O of the cross slot structure 30 ₁ Corresponds to the third connecting rod L ₃ And a fourth connecting rod L ₄ Is provided; the two eccentric portions 11 of the crankshaft 10 serve as first connecting rods L, respectively ₁ And a second connecting rod L ₂ The two limiting channels 31 of the cross slot structure 30 are respectively used as the third connecting rod L ₃ And a fourth connecting rod L ₄ And a first link L ₁ And a second connecting rod L ₂ So that the eccentric portion 11 of the crankshaft 10 drives the corresponding slide block 40 around the axis O of the crankshaft 10 while the crankshaft 10 rotates ₀ The revolution, simultaneously the slider 40 can rotate relative to the eccentric part 11, and the relative rotation speed of the two sliders is the same, because the first slider 40 and the second slider 40 respectively reciprocate in the two corresponding limiting channels 31 and drive the cross groove structure 30 to do circular motion, the two limiting channels 31 of the cross groove structure 30 limit the motion direction of the two sliders 40 always have the phase difference of the second included angle B, when one of the two sliders 40 is at the dead point position, the eccentric part 11 for driving the other of the two sliders 40 has the maximum driving torque, and the eccentric part 11 with the maximum driving torque can normally drive the corresponding slider 40 to rotate, thereby driving the cross groove structure 30 to rotate through the slider 40, further driving the slider 40 at the dead point position to continue to rotate through the cross groove structure 30, realizing the stable operation of the fluid machinery, avoiding the dead point position of the motion mechanism, improving the motion reliability of the fluid machinery, and thus ensuring the working reliability of the heat exchange equipment.

In the present application, the maximum arm of the driving torque of the eccentric portion 11 is 2e.

In this movement method, the running track of the slider 40 is a circle, and the circle is about the axis O of the crankshaft 10 ₀ With the line O as the center of a circle ₀ O ₁ Is a radius.

In this application, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 times to complete 4 intake and exhaust processes.

An alternative embodiment will be described in detail below to describe the structure of the fluid machine in order to better illustrate the method of operation of the fluid machine by means of its constructional features.

Alternatively, the bearing 200 is a cage needle+inner ring bearing, or a ball bearing, but may be another bearing capable of achieving this function.

As shown in fig. 6, the height H1 of the bearing 200 and the height H2 of the cylinder liner 20 satisfy: H2-H1 is more than or equal to 0.003mm and less than or equal to 0.1mm. In this way, by optimizing the difference between the height H1 of the bearing 200 and the height H2 of the cylinder liner 20, the cross groove structure 30 is effectively prevented from tilting, and good lubrication between the cross groove structure 30 and the cylinder liner 20 is ensured, so that mechanical friction power consumption between the cross groove structure 30 and the cylinder liner 20 is reduced, the performance of the compressor is improved, and the operational reliability of the compressor is improved.

In this embodiment, since the height H1 of the bearing 200 is similar to the height H2 of the cylinder liner 20, and in order to ensure the reliability of the bearing 200 supporting the cross groove structure 30, the air intake and exhaust ports are not formed in the radial direction of the bearing 200, specifically, as shown in fig. 10, the fluid machine includes two flanges 50, the two flanges 50 are respectively assembled at two axial ends of the cylinder liner 20, the two flanges 50 are respectively provided with an air intake channel 54, the two air intake channels 54 are respectively communicated with the two limiting channels 31, the two flanges 50 are respectively provided with an air exhaust channel 51, and a phase difference exists between the air intake channel 54 and the air exhaust channel 51 on the same flange 50. In this way, the integrity of the bearing 200 is ensured while the reliability of the intake and exhaust of the cylinder liner 20 is ensured.

As shown in fig. 1, the two eccentric portions 11 have a phase difference of a first included angle a, the eccentric amounts of the two eccentric portions 11 are equal, and the extending directions of the two limiting channels 31 have a phase difference of a second included angle B, wherein the first included angle a is twice the second included angle B.

As shown in fig. 3 to 21, the fluid machine further includes a flange 50, the flange 50 is disposed at an axial end portion of the cylinder liner 20, the crankshaft 10 is disposed concentrically with the flange 50, the cross groove structure 30 is disposed coaxially with the cylinder liner 20, an assembly eccentricity of the crankshaft 10 and the cross groove structure 30 is determined by a relative positional relationship between the flange 50 and the cylinder liner 20, wherein the flange 50 is fixed on the cylinder liner 20 by a fastener 90, a relative position of an axial center of the flange 50 and an axial center of an inner ring of the cylinder liner 20 is controlled by aligning the flange 50, and a relative position of the axial center of the flange 50 and the axial center of the inner ring of the cylinder liner 20 determines a relative position of the axial center of the crankshaft 10 and the axial center of the cross groove structure 30, and an eccentric amount of the eccentric portion 11 is equal to an assembly eccentricity of the crankshaft 10 and the cylinder liner 20 by an essence of aligning the flange 50.

Specifically, as shown in fig. 9, the eccentric amounts of the two eccentric portions 11 are equal to e, as shown in fig. 10, the fitting eccentric amount between the crankshaft 10 and the cylinder liner 20 is e (since the cross groove structure 30 is coaxially provided with the cylinder liner 20, the fitting eccentric amount between the crankshaft 10 and the cross groove structure 30, that is, the fitting eccentric amount between the crankshaft 10 and the cylinder liner 20), and the flange 50 includes an upper flange 52 and a lower flange 53, as shown in fig. 12, the distance between the inner ring axis of the cylinder liner 20 and the inner ring axis of the lower flange 53 is e, that is, equal to the eccentric amount of the eccentric portion 11.

Optionally, a first assembly gap is provided between the crankshaft 10 and the flange 50, the first assembly gap being in the range of 0.005mm to 0.05mm.

Preferably, the first assembly gap ranges from 0.01 to 0.03mm.

As shown in fig. 4, 5, and 7 to 10, the shaft body portion 12 of the crankshaft 10 is integrally formed, and the shaft body portion 12 has only one axial center. Thus, the one-time molding of the shaft body part 12 is facilitated, and the processing and manufacturing difficulty of the shaft body part 12 is reduced.

In an embodiment, not shown in the drawings, the shaft body 12 of the crankshaft 10 includes a first section and a second section connected along an axial direction thereof, the first section and the second section are coaxially disposed, and the two eccentric portions 11 are disposed on the first section and the second section, respectively.

Optionally, the first section is detachably connected to the second section. In this way, convenience in assembling and disassembling the crankshaft 10 is ensured.

As shown in fig. 4, 5, and 7 to 10, the shaft body portion 12 of the crankshaft 10 is integrally formed with the eccentric portion 11. Thus, the crankshaft 10 is formed at one time, and the difficulty in machining and manufacturing the crankshaft 10 is reduced.

In an embodiment not shown in the present application, the shaft portion 12 of the crankshaft 10 is detachably connected to the eccentric portion 11. In this way, the installation and the removal of the eccentric portion 11 are facilitated.

As shown in fig. 5, both ends of the limiting passage 31 penetrate to the outer peripheral surface of the intersecting groove structure 30. Thus, the difficulty in manufacturing the cross groove structure 30 is advantageously reduced.

Alternatively, the two sliders 40 are respectively arranged concentrically with the two eccentric portions 11, the sliders 40 do circular motion around the eccentric portions 11, and a first rotation gap is formed between the hole wall of the through hole 41 and the eccentric portions 11, and the range of the first rotation gap is 0.005 mm-0.05 mm.

As shown in fig. 4, 5, 10 to 12, 16 and 17, the outer circumference of the cylinder liner 20 has a circumferential collar 28, and a plurality of elongated holes 281 are provided on the circumferential collar 28 at intervals. Thus, the elongated hole 281 functions as an oil return for the ambient space.

It should be noted that, in the present application, the first included angle a is 160 degrees to 200 degrees; the second included angle B is 80-100 degrees. In this way, the relationship that the first angle a is twice the second angle B is satisfied.

Preferably, the first included angle a is 160 degrees and the second included angle B is 80 degrees.

Preferably, the first included angle a is 165 degrees and the second included angle B is 82.5 degrees.

Preferably, the first included angle a is 170 degrees and the second included angle B is 85 degrees.

Preferably, the first included angle a is 175 degrees and the second included angle B is 87.5 degrees.

Preferably, the first included angle a is 180 degrees and the second included angle B is 90 degrees.

Preferably, the first included angle a is 185 degrees and the second included angle B is 92.5 degrees.

Preferably, the first included angle a is 190 degrees and the second included angle B is 95 degrees.

Preferably, the first included angle a is 195 degrees and the second included angle B is 97.5 degrees.

In the present application, the eccentric portion 11 has an arc surface, and the central angle of the arc surface is 180 degrees or more. In this way, the arc surface of the eccentric portion 11 is ensured to be able to exert an effective driving force on the slider 40, thereby ensuring the movement reliability of the slider 40.

As shown in fig. 4, 5, and 7 to 10, the eccentric portion 11 is cylindrical.

Alternatively, the proximal end of the eccentric 11 is flush with the outer circumference of the shaft body portion 12 of the crankshaft 10.

Alternatively, the proximal end of the eccentric portion 11 protrudes from the outer circumference of the shaft body portion 12 of the crankshaft 10.

Alternatively, the proximal end of the eccentric portion 11 is located inside the outer circumference of the shaft body portion 12 of the crankshaft 10.

It should be noted that, in an embodiment not shown in the present application, the slider 40 includes a plurality of sub-structures, and the plurality of sub-structures are spliced to form the through hole 41.

As shown in fig. 4, 5, and 7 to 10, two eccentric portions 11 are provided at intervals in the axial direction of the crankshaft 10. In this way, ensuring the separation distance between the two eccentric portions 11 during the assembly of the crankshaft 10, the cylinder liner 20 and the two sliders 40 can provide an assembly space for the cylinder liner 20 to ensure assembly convenience.

As shown in fig. 5, the cross groove structure 30 has a center hole 32, and two limiting passages 31 communicate through the center hole 32, and the diameter of the center hole 32 is larger than the diameter of the shaft body portion 12 of the crankshaft 10. In this way, it is ensured that the crankshaft 10 can pass smoothly through the center hole 32.

Alternatively, the bore diameter of the central bore 32 is larger than the diameter of the eccentric 11. In this way, it is ensured that the eccentric portion 11 of the crankshaft 10 can smoothly pass through the center hole 32.

As shown in fig. 13, the projection of the slider 40 in the axial direction of the through hole 41 has two relatively parallel straight line segments and an arc segment connecting the ends of the two straight line segments. The limiting channel 31 has a set of oppositely disposed first sliding surfaces in sliding contact with the slider 40, the slider 40 has a second sliding surface cooperating with the first sliding surfaces, the slider 40 has a pressing surface 42 facing the end of the limiting channel 31, the pressing surface 42 acts as the head of the slider 40, the two second sliding surfaces are connected by the pressing surface 42, and the pressing surface 42 faces the variable volume chamber 311. In this way, the projection of the second sliding surface of the slider 40 in the axial direction of the through hole 41 thereof is a straight line segment, while the projection of the pressing surface 42 of the slider 40 in the axial direction of the through hole 41 thereof is an arc segment.

Specifically, the pressing surface 42 is a cambered surface,the distance between the center of the arc surface and the center of the through hole 41 is equal to the eccentric amount of the eccentric portion 11. In FIG. 13, the center of the through hole 41 of the slider 40 is O _{Sliding block} The distances between the centers of the two cambered surfaces and the center of the through hole 41 are e, that is, the eccentric amount of the eccentric portion 11, and the broken line X in fig. 13 indicates the circle in which the centers of the two cambered surfaces are located.

In the present application, as shown in fig. 5, the slider 40 has a pressing surface 42 facing the end of the limiting passage 31, the pressing surface 42 being a head of the slider 40, and the pressing surface 42 facing the variable volume chamber 311.

Alternatively, the radius of curvature of the arcuate surface is equal to the radius of the inner circle of the liner 20.

Alternatively, the radius of curvature of the arcuate surface has a difference from the radius of the inner circle of the liner 20 in the range of-0.05 mm to 0.025mm.

Preferably, the difference ranges from-0.02 to 0.02mm.

In the present application, the projected area S of the pressing surface 42 in the sliding direction of the slider 40 _{Sliding block} The area of the compression exhaust port with the cylinder sleeve 20 is S _{Row of rows} The following are satisfied: s is S _{Sliding block} /S _{Row of rows} The value of (2) is 8 to 25.

Preferably S _{Sliding block} /S _{Row of rows} The value of (2) is 12 to 18.

It should be noted that, the fluid machine shown in this embodiment is a compressor, as shown in fig. 3, the compressor includes a dispenser member 80, a housing assembly 81, a motor assembly 82, a pump body assembly 83, an upper cover assembly 84, and a lower cover assembly 85, where the dispenser member 80 is disposed outside the housing assembly 81, the upper cover assembly 84 is assembled at the upper end of the housing assembly 81, the lower cover assembly 85 is assembled at the lower end of the housing assembly 81, the motor assembly 82 and the pump body assembly 83 are both located inside the housing assembly 81, and the motor assembly 82 is located above the pump body assembly 83, or the motor assembly 82 is located below the pump body assembly 83. The pump body assembly 83 of the compressor includes the crankshaft 10, cylinder liner 20, cross-slot structure 30, slide 40, upper flange 52 and lower flange 53 described above.

Optionally, the above components are connected by welding, hot sheathing, or cold pressing.

The entire pump body assembly 83 is assembled as follows: the lower flange 53 is fixed on the cylinder sleeve 20, the two sliding blocks 40 are respectively placed in the two corresponding limiting channels 31, the two eccentric parts 11 of the crankshaft 10 respectively extend into the two through holes 41 of the corresponding two sliding blocks 40, the assembled crankshaft 10, the cross groove structure 30 and the two sliding blocks 40 are placed in the cylinder sleeve 20, one end of the crankshaft 10 is mounted on the lower flange 53, and the other end of the crankshaft 10 is arranged through the upper flange 52, and particularly, see fig. 4 and 5.

It should be noted that, in the present embodiment, the enclosed space enclosed by the slide block 40, the limiting channel 31, the cylinder liner 20 and the upper flange 52 (or the lower flange 53) is the variable volume cavity 311, the pump body assembly 83 has 4 variable volume cavities 311 altogether, in the process of rotating the crankshaft 10, the crankshaft 10 rotates 2 circles, and a single variable volume cavity 311 completes 1 air intake and exhaust process, and for the compressor, the crankshaft 10 rotates 2 circles to complete 4 air intake and exhaust processes in total.

As shown in fig. 18 to 20, the slider 40 rotates relative to the cylinder liner 20 while reciprocating in the limiting passage 31, in fig. 18, the variable volume chamber 311 increases in the process of rotating the slider 40 clockwise from 0 degrees to 180 degrees, the variable volume chamber 311 communicates with the suction chamber of the cylinder liner 20 in the process of increasing the variable volume chamber 311, when the slider 40 rotates to 180 degrees, the volume of the variable volume chamber 311 reaches the maximum value, the variable volume chamber 311 at this time is separated from the suction chamber, thereby completing the suction operation, in fig. 19 and 20, the variable volume chamber 311 decreases in the process of continuing to rotate from 180 degrees to 360 degrees in the clockwise direction, the slider 40 compresses the gas in the variable volume chamber 311, when the slider 40 rotates until the variable volume chamber 311 communicates with the compression exhaust port 22, and when the gas in the variable volume chamber 311 reaches the exhaust pressure, the exhaust valve plate of the exhaust valve assembly opens, and the exhaust operation starts until the next cycle is entered after the compression is completed.

As shown in fig. 18 to 20, the slider 40 rotates 1 turn, and the corresponding crankshaft 10 rotates 2 turns.

As shown in fig. 4, 10 and 14 to 20, the fluid machine includes two flanges 50, the flanges 50 include an upper flange 52 and a lower flange 53, the two flanges 50 are respectively assembled at two axial ends of the cylinder liner 20, the two flanges 50 are respectively provided with an air inlet channel 54, the two air inlet channels 54 are respectively communicated with the two limiting channels 31, the two flanges 50 are respectively provided with an air outlet channel 51, and a phase difference exists between the air inlet channel 54 and the air outlet channel 51 on the same flange 50. In this way, the integrity of the bearing 200 is ensured while the reliability of the intake and exhaust of the cylinder liner 20 is ensured.

As shown in fig. 10 and 17, the intake passage 54 includes a first intake passage section 541 and a second intake passage section 542 that are sequentially communicated, the first intake passage section 541 extending in the radial direction of the flange 50, and the second intake passage section 542 extending in the axial direction of the flange 50. In this way, the communication reliability of the intake passage 54 with the variable volume chamber 311 is ensured.

As shown in fig. 17, an exhaust groove 55 is provided on the end surface of the flange 50 facing away from the cylinder liner 20, and an exhaust communication port 551 is provided at the bottom of the exhaust groove 55 and communicates with the stopper passage 31, the exhaust communication port 551 extending in the axial direction of the flange 50. In this way, the exhaust reliability of the cylinder liner 20 is ensured.

As shown in fig. 17, the end of the air intake passage 54 is an air intake communication port, the initial end of the air exhaust passage 51 is an air exhaust communication port 551, and when any slider 40 is at the air intake position, the air intake communication port is communicated with the corresponding variable volume chamber 311; when any one of the sliders 40 is at the exhaust position, the corresponding volume chamber 311 is in communication with the exhaust communication port 551.

Other use occasions: the compressor can be used as an expander by exchanging positions of the suction port and the exhaust port. That is, the high-pressure gas is introduced into the exhaust port of the compressor as the intake port of the expander, and the other pushing mechanism rotates, and the gas is discharged through the intake port of the compressor (the exhaust port of the expander) after expansion.

When the fluid machine is an expander, the tail end of the air inlet channel 54 is an air inlet communication port, the initial end of the air outlet channel 51 is an air outlet communication port 551, and when any slide block 40 is at the air inlet position, the air outlet communication port 551 is communicated with the corresponding volume cavity 311; when any one of the sliders 40 is at the exhaust position, the corresponding volume chamber 311 is communicated with the intake communication port.

As shown in fig. 22 to 25, the projection of the slider 40 in the sliding direction is adapted to the cross section of the limiting channel 31, wherein fig. 22 is a direction slider chamfer and a corresponding cross groove structure 30, fig. 23 is a trapezoidal slider and a corresponding cross groove structure 30, fig. 24 is a trapezoidal slider chamfer and a corresponding cross groove structure 30, and fig. 25 is a semicircular+straight-sided slider and a corresponding cross groove structure 30.

It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of 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 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

1. A fluid machine having a bearing, comprising:

a crankshaft (10), the crankshaft (10) being provided with two eccentric portions (11) along its axial direction;

the crankshaft (10) and the cylinder sleeve (20) are eccentrically arranged, and the eccentric distance is fixed;

the bearing (200) is arranged in the cylinder sleeve (20), and the outer ring of the bearing (200) is attached to the inner wall of the cylinder sleeve (20);

The cross groove structure (30), the cross groove structure (30) is rotatably arranged in the cylinder sleeve (20), the outer peripheral surface of the cross groove structure (30) is attached to the inner ring of the bearing (200), the ratio between the height H1 of the bearing (200) and the height H2 of the cylinder sleeve (20) is more than 0.9 and less than 1, the cross groove structure (30) is provided with two limiting channels (31), the two limiting channels (31) are sequentially arranged along the axial direction of the crankshaft (10), and the extending direction of the limiting channels (31) is perpendicular to the axial direction of the crankshaft (10);

the sliding block (40), the sliding block (40) has through-hole (41), the sliding block (40) is two, two eccentric part (11) correspond to stretch into two in the through-hole (41) of sliding block (40), two sliding block (40) correspond the slip setting two in spacing passageway (31) and form variable volume chamber (311), variable volume chamber (311) are located the slip direction of sliding block (40), bent axle (10) rotate in order to drive sliding block (40) are in spacing passageway (31) reciprocating sliding is simultaneously with cross groove structure (30) interact, make cross groove structure (30) slider (40) are in cylinder liner (20) internal rotation.

2. The fluid machine according to claim 1, characterized in that between the height H1 of the bearing (200) and the height H2 of the cylinder liner (20) is: H2-H1 is more than or equal to 0.003mm and less than or equal to 0.1mm.

3. The fluid machine according to claim 1, characterized in that the two eccentric portions (11) have a phase difference of a first angle a, the eccentric amounts of the two eccentric portions (11) are equal, and the two limiting channels (31) have a phase difference of a second angle B in the extending direction, wherein the first angle a is twice the second angle B.

4. The fluid machine according to claim 1, characterized in that the eccentric amount of the eccentric portion (11) is equal to the fitting eccentric amount of the crankshaft (10) and the cylinder liner (20).

5. The fluid machine according to claim 1, wherein both ends of the limiting passage (31) penetrate to the outer peripheral surface of the intersecting groove structure (30).

6. The fluid machine according to claim 1, wherein two sliding blocks (40) are arranged concentrically with two eccentric portions (11), the sliding blocks (40) do circular motion around the eccentric portions (11), a first rotating gap is arranged between the hole wall of the through hole (41) and the eccentric portions (11), and the first rotating gap ranges from 0.005mm to 0.05mm.

7. The fluid machine according to claim 1, wherein the cylinder liner (20) has a circumferential collar (28) at its outer periphery, and a plurality of spaced apart elongated holes (281) are provided in the circumferential collar (28).

8. A fluid machine according to claim 3, wherein the first included angle a is 160-200 degrees; the second included angle B is 80-100 degrees.

9. The fluid machine according to claim 1, further comprising a flange (50), said flange (50) being arranged at an axial end of said cylinder liner (20), said crankshaft (10) being arranged concentrically with said flange (50).

10. The fluid machine according to claim 9, characterized in that there is a first assembly gap between the crankshaft (10) and the flange (50), the first assembly gap being in the range of 0.005mm to 0.05mm.

11. The fluid machine of claim 10, wherein the first assembly gap is in the range of 0.01 to 0.03mm.

12. The fluid machine according to claim 1, wherein the eccentric portion (11) has an arc surface, and a central angle of the arc surface is 180 degrees or more.

13. A fluid machine according to claim 1, characterized in that the eccentric (11) is cylindrical.

14. The fluid machine of claim 13, wherein the fluid machine is further configured to,

the proximal end of the eccentric part (11) is flush with the outer circle of the shaft body part (12) of the crankshaft (10); or alternatively, the first and second heat exchangers may be,

The proximal end of the eccentric part (11) protrudes out of the outer circle of the shaft body part (12) of the crankshaft (10); or alternatively, the first and second heat exchangers may be,

the proximal end of the eccentric portion (11) is located inside the outer circumference of the shaft body portion (12) of the crankshaft (10).

15. The fluid machine according to claim 1, wherein the slider (40) comprises a plurality of substructures, and wherein the plurality of substructures are spliced to define the through hole (41).

16. Fluid machine according to claim 1, characterized in that two of the eccentric parts (11) are arranged at intervals in the axial direction of the crankshaft (10).

17. The fluid machine according to claim 1, characterized in that the cross-slot structure (30) has a central bore (32), through which central bore (32) two of the limiting channels (31) communicate, the bore diameter of the central bore (32) being larger than the diameter of the shaft body part (12) of the crankshaft (10).

18. The fluid machine according to claim 17, characterized in that the bore diameter of the central bore (32) is larger than the diameter of the eccentric section (11).

19. Fluid machine according to claim 1, characterized in that the projection of the slider (40) in the axial direction of the through hole (41) has two relatively parallel straight segments and an arc segment connecting the ends of the two straight segments.

20. The fluid machine according to claim 1, characterized in that the slide (40) has a pressing surface (42) facing the end of the limiting channel (31), the pressing surface (42) acting as a head of the slide (40), the pressing surface (42) facing the variable volume chamber (311).

21. The fluid machine according to claim 20, wherein the pressing surface (42) is an arc surface, and a distance between an arc center of the arc surface and a center of the through hole (41) is equal to an eccentric amount of the eccentric portion (11).

22. The fluid machine of claim 21, wherein the fluid machine is further configured to,

the radius of curvature of the cambered surface is equal to the radius of the inner circle of the cylinder sleeve (20); or alternatively, the first and second heat exchangers may be,

the radius of curvature of the cambered surface and the radius of the inner circle of the cylinder sleeve (20) have a difference value, and the range of the difference value is-0.05 mm-0.025 mm.

23. The fluid machine of claim 22, wherein the difference is in the range of-0.02 to 0.02mm.

24. The fluid machine according to claim 20, characterized in that the projected area S of the pressing surface (42) in the sliding direction of the slider (40) _{Sliding block} The area of the compression exhaust port with the cylinder sleeve (20) is S _{Row of rows} The following are satisfied: s is S _{Sliding block} /S _{Row of rows} The value of (2) is 8 to 25.

25. The fluid machine of claim 24, wherein S _{Sliding block} /S _{Row of rows} The value of (2) is 12 to 18.

26. The fluid machine according to claim 1, characterized in that the fluid machine comprises two flanges (50), the two flanges (50) are respectively assembled at two axial ends of the cylinder sleeve (20), the two flanges (50) are respectively provided with an air inlet channel (54), the two air inlet channels (54) are respectively communicated with the two limiting channels (31), the two flanges (50) are respectively provided with an air outlet channel (51), and a phase difference exists between the air inlet channels (54) and the air outlet channels (51) on the same flange (50).

27. The fluid machine of claim 26, wherein the intake passage (54) includes a first intake passage section (541) and a second intake passage section (542) that are in sequential communication, the first intake passage section (541) extending in a radial direction of the flange (50), the second intake passage section (542) extending in an axial direction of the flange (50).

28. The fluid machine according to claim 26, characterized in that an exhaust groove (55) is provided on a side end surface of the flange (50) facing away from the cylinder liner (20), an exhaust communication port (551) is provided at a groove bottom of the exhaust groove (55) and communicates with the limiting passage (31), and the exhaust communication port (551) extends in an axial direction of the flange (50).

29. The fluid machine according to claim 26, wherein the air intake passage (54) is terminated with an air intake communication port, the initial end of the air exhaust passage (51) is an air exhaust communication port (551),

when any sliding block (40) is positioned at an air inlet position, the air inlet communication port is communicated with the corresponding variable-volume cavity (311);

when any one of the sliding blocks (40) is at the exhaust position, the corresponding variable-volume cavity (311) is communicated with the exhaust communication port (551).

30. The fluid machine of claim 29, wherein the fluid machine is a compressor.

31. The fluid machine according to claim 26, wherein the air intake passage (54) is terminated with an air intake communication port, the initial end of the air exhaust passage (51) is an air exhaust communication port (551),

when any one of the sliding blocks (40) is at an air inlet position, the air exhaust communication port (551) is communicated with the corresponding variable-volume cavity (311);

when any sliding block (40) is at the exhaust position, the corresponding variable-volume cavity (311) is communicated with the air inlet communication port.

32. The fluid machine of claim 31, wherein the fluid machine is an expander.

33. A heat exchange device comprising a fluid machine, characterized in that the fluid machine is a fluid machine according to any one of claims 1 to 32.