CN116241468A

CN116241468A - Fluid machine and heat exchange device with bearing

Info

Publication number: CN116241468A
Application number: CN202111489274.8A
Authority: CN
Inventors: 杜忠诚; 于瑞波; 谢利昌; 李直; 张培林; 宋雪威
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: 2023-06-09

Abstract

The invention provides a fluid machine with a bearing and heat exchange equipment, wherein the fluid machine with the bearing 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; at least one bearing is arranged at the axial end face of the cylinder sleeve and positioned at the outer side of the cylinder sleeve; the crossed groove structure is rotatably arranged in the cylinder sleeve, part of the outer circumferential surface of the axial direction of the crossed groove structure is attached to the inner ring of the bearing, 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; at least one bearing is arranged at the axial end face of the cylinder sleeve and positioned at the outer side of the cylinder sleeve; the cross groove structure is rotatably arranged in the cylinder sleeve, part of the outer circumferential surface of the axial direction of the cross groove structure is attached to the inner ring of the bearing, the cross 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, only one end of the axial end part of the cylinder sleeve is provided with a bearing; or, the two ends of the axial end part of the cylinder sleeve are provided with bearings.

Further, the diameter D1 of the inner ring of the bearing and the diameter D3 of the outer circumferential surface of the cylinder liner satisfy: D1-D3 is 0.003-0.02mm.

Further, the diameter D2 of the outer peripheral surface of the cross groove structure and the diameter D3 of the inner wall surface of the cylinder liner satisfy: D2-D3 is 0.02-0.05mm.

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 cross groove structure and the cylinder sleeve are coaxially arranged, a second rotating gap is formed between the outer peripheral surface of the cross groove structure and the inner wall surface of the cylinder sleeve, and the range of the second rotating gap is 0.005-0.05 mm.

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, the crankshaft and the flange are arranged concentrically, and the flange and the cylinder sleeve are arranged eccentrically.

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, when only one end of the axial end portion of the cylinder sleeve is provided with the bearing, the fluid machine comprises two flanges which are respectively assembled at the axial end portion of the cylinder sleeve and the axial end portion of the bearing, and the cylinder sleeve is provided with a radial air suction hole and an axial flow dividing hole communicated with the radial air suction hole; the radial suction hole is communicated with a limit channel corresponding to the radial direction of the cylinder sleeve, the bearing is provided with a suction through hole communicated with the axial diversion hole, the flange on the side of the bearing is provided with a suction channel, one end of the suction channel is communicated with the suction through hole, and the other end of the suction channel is communicated with the limit channel corresponding to the bearing.

Further, the inner wall surface of the cylinder sleeve is provided with an air suction cavity, and the air suction cavity is communicated with the radial air suction hole.

Further, the suction cavity extends a first preset distance around the circumference of the inner wall surface of the cylinder sleeve to form an arc-shaped suction cavity.

Further, the cylinder sleeve is provided with a compression exhaust port, a phase difference is arranged between the compression exhaust port and the radial air suction hole, an exhaust cavity is formed in the outer wall of the cylinder sleeve, the compression exhaust port is communicated to the exhaust cavity through the inner wall of the cylinder sleeve, and the fluid machinery further comprises an exhaust valve assembly which is arranged in the exhaust cavity and corresponds to the compression exhaust port.

Further, the flange on the bearing side is provided with a flange exhaust port, the flange exhaust port is communicated with a limiting channel on the bearing, and the flange exhaust port is positioned in the inner ring side of the bearing.

Further, the tail end of the radial air suction hole is a first air inlet communication port, the tail end of the air suction channel is a second air inlet communication port, when the sliding block at the cylinder sleeve is at an air inlet position, the first air inlet communication port is communicated with the corresponding variable volume cavity, and when the sliding block at the cylinder sleeve is at an air outlet position, the corresponding variable volume cavity is communicated with the compression air outlet; when the sliding block at the bearing is at the air inlet position, the second air inlet communication port is communicated with the corresponding variable volume cavity, and when the sliding block at the bearing is at the air outlet position, the corresponding variable volume cavity is communicated with the flange air outlet.

Further, the fluid machine is a compressor.

Further, the tail end of the radial air suction hole is a first air inlet communication port, the tail end of the air suction channel is a second air inlet communication port, when the sliding block at the cylinder sleeve is at the air inlet position, the compression air outlet is communicated with the corresponding variable volume cavity, and when the sliding block at the cylinder sleeve is at the air outlet position, the corresponding variable volume cavity is communicated with the first air inlet communication port; when the sliding block at the bearing is at the air inlet position, the flange air outlet is communicated with the corresponding variable volume cavity, and when the sliding block at the bearing is at the air outlet position, the corresponding variable volume cavity is communicated with the second air inlet communication port.

Further, the fluid machine is an expander.

Further, when the bearings are arranged at the two ends of the axial end part of the cylinder sleeve, the radial air suction hole and the axial flow dividing hole communicated with the radial air suction hole are formed in the cylinder sleeve; one end of the axial flow dividing hole is communicated with one of the two limiting channels, and the other end of the axial flow dividing hole is communicated with the other of the two limiting channels.

Further, the inner wall surface of the cylinder sleeve is provided with an air suction cavity, and the air suction cavity is communicated with the axial flow dividing hole.

Further, the number of the two air suction cavities is two, the two air suction cavities are arranged at intervals along the axial direction of the cylinder sleeve, and the two air suction cavities are in one-to-one correspondence and are communicated with the two limiting channels.

Further, the cylinder sleeve is provided with a compression exhaust port, and a phase difference is arranged between the compression exhaust port and the radial suction hole.

Further, the number of the compression exhaust ports is two, the two compression exhaust ports are arranged at intervals along the axial direction of the cylinder sleeve, and the two compression exhaust ports are in one-to-one correspondence with and communicated with the two limiting channels.

Further, the tail end of the air suction cavity is an air inlet 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 compression exhaust port.

Further, the fluid machine is a compressor.

Further, the tail end of the air suction cavity is an air inlet communication port, and when any sliding block is positioned at the air inlet position, the compression air outlet 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 axial terminal surface department of cylinder liner and lie in the outside of cylinder liner for the laminating of the axial partial outer peripheral face of cross groove structure and the inner circle of bearing, like this, the outer peripheral face of cross groove structure passes through the bearing support antifriction, make between the circumference outer surface of cross groove structure and the inner wall of cylinder liner become the circumference outer surface of cross groove structure and the rolling friction of bearing by sliding friction, mechanical friction consumption has been reduced, wherein, the inner circle of bearing cooperates with cross groove structure, the inner circle of bearing cooperates with the inner wall of cylinder liner.

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 a first embodiment of the present invention;

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

FIG. 5 shows a schematic cross-sectional view of the J-J view of FIG. 4;

FIG. 6 shows a schematic cross-sectional view of the T-T view of FIG. 4;

FIG. 7 shows a schematic cross-sectional view of the view K-K of FIG. 4;

FIG. 8 shows an exploded view of the pump body assembly of FIG. 3;

FIG. 9 shows a schematic diagram of the assembled structure of the crankshaft, cross slot structure, and slider of FIG. 8;

FIG. 10 shows a schematic cross-sectional view of the crankshaft, cross slot configuration, and slider of FIG. 9;

FIG. 11 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. 9;

FIG. 12 is a schematic view showing the assembly eccentricity of the crankshaft and cylinder liner of FIG. 8;

FIG. 13 shows a schematic view of the slider of FIG. 8 in the axial direction of the through hole; the method comprises the steps of carrying out a first treatment on the surface of the

FIG. 14 shows a schematic structural view of the cylinder liner of FIG. 8;

FIG. 15 shows a schematic structural view of the cylinder liner of FIG. 14 from another perspective;

FIG. 16 is a schematic cross-sectional view of the view W-W of FIG. 15;

FIG. 17 is a schematic view showing the structure of the S-S view in FIG. 16;

fig. 18 is a schematic view showing an internal structure of a compressor according to a second embodiment of the present invention;

FIG. 19 shows a schematic cross-sectional view of the pump body assembly of FIG. 18;

fig. 20 is a schematic view showing an internal structure of a compressor according to a third embodiment of the present invention;

FIG. 21 shows a schematic cross-sectional structural view of the pump body assembly of FIG. 20;

FIG. 22 is a schematic diagram showing the mechanism of operation of a prior art compressor;

FIG. 23 is a schematic diagram showing the mechanism of operation of the compressor modified in the prior art;

FIG. 24 is a schematic view of the mechanism of operation of the compressor of FIG. 23 showing the moment arm of the drive shaft driving the slider in rotation;

fig. 25 shows a schematic view of the principle of the mechanism of operation of the compressor of fig. 23, 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; 22. a compression exhaust port; 23. an air suction cavity; 25. an exhaust chamber; 220. radial suction holes; 230. an axial flow dividing 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; 52. an upper flange; 53. a lower flange; 56. an air suction passage; 57. a flange exhaust port; 58. a cover plate;

60. an exhaust valve assembly;

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. a bearing; 201. and a suction through hole.

Detailed Description

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

In the prior art, as shown in FIG. 22, 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. 23, a method of using O ₀ As the centre of the drive shaftMovement mechanisms, i.e. cylinder centre 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.

The corresponding one set of running mechanism is proposed, including cylinder, spacing groove structure, slider and drive shaft, wherein, spacing groove structure rotationally sets up in the cylinder, and cylinder and spacing groove structure coaxial setting, i.e. cylinder center O 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. 24, 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. 25, 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; at least one bearing 200, the bearing 200 is arranged at the axial end surface of the cylinder sleeve 20 and is positioned outside the cylinder sleeve 20; the cross groove structure 30 is rotatably arranged in the cylinder sleeve 20, part of the outer circumferential surface of the axial direction of the cross groove structure 30 is attached to the inner ring of the bearing 200, 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.

Further, by disposing the bearing 200 at the axial end face of the cylinder liner 20 and outside the cylinder liner 20 such that part of the axial outer peripheral surface of the intersecting groove structure 30 is fitted with the inner ring of the bearing 200, the outer peripheral surface 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 to 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 with the intersecting groove structure 30 and the inner ring of the bearing 200 is fitted with 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 Circular movement is carried out for the circle center, and the secondCenter O of each slider 40 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 The eccentric distance between them, the crankshaft 10 rotates to drive the second slider 40 to do circular motion, and the second slider 40 interacts with the cross slot structure 30 and slides reciprocally in the limiting channel 31 of the cross slot structure 30.

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 also comprises the rotation angular speed of the sliding block 40 relative to the eccentric part 11 and the rotation angular speed of the sliding block 40 around the axis of the crankshaft 10O 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.

Three alternative embodiments are provided below to describe the structure of the fluid machine in detail, so that the method of operation of the fluid machine can be better illustrated by the structural features.

Example 1

As shown in fig. 3 to 17, in the present embodiment, only one end of the axial end portion of the cylinder liner 20 is provided with the bearing 200, and the bearing 200 is located on the upper side of one end of the axial end portion of the cylinder liner 20.

Alternatively, the diameter D1 of the inner ring of the bearing 200 and the diameter D3 of the outer circumferential surface of the cylinder liner 20 satisfy: D1-D3 is 0.003-0.02mm.

Alternatively, the diameter D2 of the outer peripheral surface of the intersecting groove structure 30 and the diameter D3 of the inner wall surface of the cylinder liner 20 satisfy: D2-D3 is 0.02-0.05mm.

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 17, 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. 11, the eccentric amounts of the two eccentric portions 11 are equal to e, and as shown in fig. 12, the fitting eccentric amount between the crankshaft 10 and the cylinder liner 20 is e (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, since the cross groove structure 30 is disposed coaxially with the cylinder liner 20), and the flange 50 includes an upper flange 52 and a lower flange 53.

As shown in fig. 8, both ends of the stopper 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.

As shown in fig. 8 to 11, 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. 8 to 11, 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.

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.

Alternatively, the cross groove structure 30 is coaxially disposed with the cylinder liner 20, and a second rotation gap is provided between the outer circumferential surface of the cross groove structure 30 and the inner wall surface of the cylinder liner 20, and the second rotation gap ranges from 0.005mm to 0.05mm.

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.

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.

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. 8 to 11, the eccentric portion 11 is cylindrical.

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

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

Alternatively, the proximal end of the eccentric portion 11 is located inside the outer circumference of the shaft body portion 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. 8 to 11, 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. 8, 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 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. 12, a schematic diagram of the assembly eccentricity of the crankshaft 10 and the cylinder liner 20 is shown, where reference numeral U denotes the center of the eccentric portion 11 of the crankshaft 10, reference numeral P denotes the center of the cylinder liner 20, and reference numeral Z denotes the center of the shaft body portion 12 of the crankshaft 10.

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 an arc surface, and the distance between the arc 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.

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.

Alternatively, 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 22 with the cylinder liner 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. 5, 7, and 14 to 17, the fluid machine includes two flanges 50, the two flanges 50 being respectively fitted to an axial end of the cylinder liner 20 and an axial end of the bearing 200, the cylinder liner 20 being provided with a radial suction hole 220 and an axial distribution hole 230 communicating with the radial suction hole 220; wherein, the radial suction hole 220 is communicated with the limit channel 31 corresponding to the radial direction of the cylinder sleeve 20, the bearing 200 is provided with a suction through hole 201 for communicating with the axial flow dividing hole 230, the flange 50 positioned at the side of the bearing 200 is provided with a suction channel 56, one end of the suction channel 56 is communicated with the suction through hole 201, and the other end of the suction channel 56 is communicated with the limit channel 31 corresponding to the position of the bearing 200. In this way, the suction reliability of the compressor is ensured.

It should be noted that, in the present embodiment, the flange 50 further includes a cover plate 58, and the cover plate 58 is disposed at a processing opening of the side of the air intake channel 56 away from the cylinder liner 20, so as to seal the air intake channel 56, and ensure that the air can smoothly enter the limiting channel 31 at the bearing 200 from the air intake through hole 201 through the air intake channel 56.

As shown in fig. 1 to 17, the inner wall surface of the cylinder liner 20 has a suction chamber 23, and the suction chamber 23 communicates with a radial suction hole 220. In this way, it is ensured that the suction chamber 23 can store a large amount of gas, so that the variable volume chamber 311 can be filled with suction gas, thereby enabling the compressor to be capable of sucking gas in a sufficient amount, and when the suction gas is insufficient, the stored gas can be timely supplied to the variable volume chamber 311, so as to ensure the compression efficiency of the compressor.

Alternatively, the suction chambers 23 are cavities formed by hollowing out the inner wall surface of the cylinder sleeve 20 along the radial direction, and the number of the suction chambers 23 can be 1 or 2.

Specifically, the suction chamber 23 extends a first preset distance around the circumference of the inner wall surface of the cylinder liner 20 to constitute an arc-shaped suction chamber 23. In this way, it is ensured that the volume of the suction chamber 23 is sufficiently large to store a large amount of gas.

As shown in fig. 6, 15 and 17, the cylinder liner 20 is provided with a compression exhaust port 22, a phase difference is formed between the compression exhaust port 22 and a radial air suction hole 220, an exhaust cavity 25 is formed in the outer wall of the cylinder liner 20, the compression exhaust port 22 is communicated to the exhaust cavity 25 by the inner wall of the cylinder liner 20, the fluid machine further comprises an exhaust valve assembly 60, and the exhaust valve assembly 60 is arranged in the exhaust cavity 25 and corresponds to the compression exhaust port 22.

Optionally, the exhaust valve assembly 60 is mounted to the cylinder liner 20 by fasteners.

As shown in fig. 7, the flange 50 on the side of the bearing 200 is provided with a flange exhaust port 57, the flange exhaust port 57 communicating with the limiting passage 31 at the bearing 200, the flange exhaust port 57 being located inside the inner ring side of the bearing 200. In this way, the bearing 200 is prevented from shielding the flange exhaust port 57, thereby ensuring the exhaust reliability of the compressor.

It should be noted that, in the embodiment, the end of the radial air suction hole 220 is a first air inlet communication port, the end of the air suction channel 56 is a second air inlet communication port, when the sliding block 40 at the cylinder sleeve 20 is at the air inlet position, the first air inlet communication port is communicated with the corresponding variable volume cavity 311, and when the sliding block 40 at the cylinder sleeve 20 is at the air outlet position, the corresponding variable volume cavity 311 is communicated with the compression air outlet 22; when the slider 40 at the bearing 200 is at the intake position, the second intake communication port is in communication with the corresponding variable-volume chamber 311, and when the slider 40 at the bearing 200 is at the exhaust position, the corresponding variable-volume chamber 311 is in communication with the flange exhaust port 57.

The operation of the compressor is described in detail below:

as shown in fig. 3, the motor assembly 82 drives the crankshaft 10 to rotate, two eccentric parts 11 of the crankshaft 10 respectively drive two corresponding sliding blocks 40 to move, the sliding blocks 40 revolve around the axis of the crankshaft 10 and simultaneously, the sliding blocks 40 rotate relative to the eccentric parts 11, the sliding blocks 40 reciprocate along the limiting channels 31 and drive the cross groove structure 30 to rotate in the cylinder sleeve 20, and the sliding blocks 40 revolve and simultaneously reciprocate along the limiting channels 31 to form a cross sliding block mechanism movement mode.

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 radial air suction hole 220 is a first air inlet communication port, the tail end of the air suction channel 56 is a second air inlet communication port, when the sliding block 40 at the cylinder sleeve 20 is at an air inlet position, the compression air outlet 22 is communicated with the corresponding variable volume cavity 311, and when the sliding block 40 at the cylinder sleeve 20 is at an air outlet position, the corresponding variable volume cavity 311 is communicated with the first air inlet communication port; when the slider 40 at the bearing 200 is at the intake position, the flange exhaust port 57 is in communication with the corresponding variable volume chamber 311, and when the slider 40 at the bearing 200 is at the exhaust position, the corresponding variable volume chamber 311 is in communication with the second intake communication port.

Example two

As shown in fig. 18 and 19, one end of the axial end portion of the cylinder liner 20 is provided with a bearing 200. The present embodiment differs from the first embodiment in that the bearing 200 of the present embodiment is located on the lower side of the axial end portion of the cylinder liner 20.

It should be noted that, the relative positions of the cylinder liner 20 and the bearing 200 in the present embodiment are merely different from each other in the vertical position, and the air intake and exhaust method in the first embodiment is also applicable to the second embodiment.

Example III

As shown in fig. 20 and 21, when both ends of the axial end portion of the cylinder liner 20 are provided with bearings 200, the cylinder liner 20 is provided with radial suction holes 220 and axial distribution holes 230 communicating with the radial suction holes 220; wherein one end of the axial flow diversion hole 230 is communicated with one of the two limiting channels 31, and the other end of the axial flow diversion hole 230 is communicated with the other of the two limiting channels 31.

As shown in fig. 21, the inner wall surface of the cylinder liner 20 has a suction chamber 23, and the suction chamber 23 communicates with an axial flow dividing hole 230.

Alternatively, the suction chamber 23 extends a first predetermined distance around the circumference of the inner wall surface of the cylinder liner 20 to constitute an arc-shaped suction chamber 23.

As shown in fig. 21, two air suction cavities 23 are arranged at intervals along the axial direction of the cylinder sleeve 20, and the two air suction cavities 23 are in one-to-one correspondence and communicated with the two limiting channels 31.

It should be noted that, in the present embodiment, the cylinder liner 20 has a compression exhaust port 22, and a phase difference is provided between the compression exhaust port 22 and the radial suction hole 220 (the position and the opening manner of the compression exhaust port 22 on the cylinder liner 20 in the present embodiment are the same as those of the compression exhaust port 22 in fig. 17 in the first embodiment, and are not repeated here).

Optionally, two compression exhaust ports 22 are arranged at intervals along the axial direction of the cylinder sleeve 20, and the two compression exhaust ports 22 are in one-to-one correspondence and communicated with the two limiting channels 31.

When the fluid machine is a compressor, the end of the suction chamber 23 is an air inlet communication port, and when any slide block 40 is at the air inlet position, the air inlet communication port is communicated with the corresponding volume chamber 311; when any one of the sliders 40 is in the discharge position, the corresponding volume chamber 311 is in communication with the compression discharge port 22.

When the fluid machine is an expander, the end of the air suction chamber 23 is an air inlet communication port, and when any slider 40 is at the air inlet position, the compression air outlet 22 is communicated with the corresponding volume chamber 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.

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;

-a bearing (200), at least one bearing (200), the bearing (200) being arranged at an axial end face of the cylinder liner (20) and being located outside the cylinder liner (20);

the cross groove structure (30), the cross groove structure (30) is rotatably arranged in the cylinder sleeve (20), part of the outer circumferential surface of the axial direction of the cross groove structure (30) is attached to the inner ring of the bearing (200), 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. A fluid machine as claimed in claim 1, wherein,

-only one end of the axial end of the cylinder liner (20) is provided with the bearing (200); or alternatively, the first and second heat exchangers may be,

the bearings (200) are arranged at both ends of the axial end part of the cylinder sleeve (20).

3. The fluid machine according to claim 1, characterized in that the diameter D1 of the inner ring of the bearing (200) and the diameter D3 of the outer circumferential surface of the cylinder liner (20) satisfy: D1-D3 is 0.003-0.02mm.

4. The fluid machine according to claim 1, wherein a diameter D2 of the outer peripheral surface of the intersecting groove structure (30) and a diameter D3 of the inner wall surface of the cylinder liner (20) satisfy: D2-D3 is 0.02-0.05mm.

5. 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.

6. 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).

7. 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).

8. 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.

9. The fluid machine according to claim 1, wherein the cross groove structure (30) is coaxially arranged with the cylinder liner (20), and a second rotational gap is provided between an outer circumferential surface of the cross groove structure (30) and an inner wall surface of the cylinder liner (20), and the second rotational gap ranges from 0.005mm to 0.05mm.

10. The fluid machine of claim 5, wherein the first included angle a is 160 degrees to 200 degrees; the second included angle B is 80-100 degrees.

11. 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), said flange (50) being arranged eccentrically with respect to said cylinder liner (20).

12. The fluid machine according to claim 11, characterized in that 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.

13. The fluid machine of claim 12, wherein the first assembly gap is in the range of 0.01 to 0.03mm.

14. 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.

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

16. The fluid machine of claim 15, 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 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 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 of the crankshaft (10).

17. 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).

18. 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).

19. The fluid machine according to claim 1, characterized in that the cross-slot structure (30) has a central hole (32), through which central hole (32) two limit channels (31) communicate, the central hole (32) having a larger bore diameter than the shaft portion of the crankshaft (10).

20. The fluid machine according to claim 19, characterized in that the bore diameter of the central bore (32) is larger than the diameter of the eccentric portion (11).

21. 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.

22. 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).

23. The fluid machine according to claim 22, 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).

24. The fluid machine of claim 23, 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.

25. The fluid machine of claim 24, wherein the difference is in the range of-0.02 to 0.02mm.

26. The fluid machine according to claim 22, 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 (22) 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.

27. The fluid machine of claim 26, wherein S _{Sliding block} /S _{Row of rows} The value of (2) is 12 to 18.

28. A fluid machine as claimed in claim 2, wherein,

when only one end of the axial end portion of the cylinder sleeve (20) is provided with the bearing (200), the fluid machine comprises two flanges (50), the two flanges (50) are respectively assembled at the axial end portion of the cylinder sleeve (20) and the axial end portion of the bearing (200), and the cylinder sleeve (20) is provided with a radial air suction hole (220) and an axial flow dividing hole (230) communicated with the radial air suction hole (220);

The radial suction hole (220) is communicated with the limit channel (31) corresponding to the cylinder sleeve (20) in the radial direction, the bearing (200) is provided with a suction through hole (201) communicated with the axial flow dividing hole (230), the flange (50) positioned on the side of the bearing (200) is provided with a suction channel (56), one end of the suction channel (56) is communicated with the suction through hole (201), and the other end of the suction channel (56) is communicated with the limit channel (31) corresponding to the position of the bearing (200).

29. The fluid machine according to claim 28, wherein the inner wall surface of the cylinder liner (20) has a suction chamber (23), the suction chamber (23) being in communication with the radial suction holes (220).

30. The fluid machine according to claim 29, wherein the suction chamber (23) extends a first predetermined distance around the circumference of the inner wall surface of the cylinder liner (20) to form an arc-shaped suction chamber (23).

31. The fluid machine of claim 28, wherein the cylinder liner (20) has a compression exhaust port (22), and a phase difference exists between the compression exhaust port (22) and the radial suction hole (220), an exhaust cavity (25) is formed in an outer wall of the cylinder liner (20), the compression exhaust port (22) is communicated to the exhaust cavity (25) by an inner wall of the cylinder liner (20), the fluid machine further comprises an exhaust valve assembly (60), and the exhaust valve assembly (60) is disposed in the exhaust cavity (25) and corresponds to the compression exhaust port (22).

32. The fluid machine according to claim 31, characterized in that the flange (50) at the side of the bearing (200) is provided with a flange exhaust port (57), the flange exhaust port (57) being in communication with the limiting channel (31) at the bearing (200), the flange exhaust port (57) being located inside the inner ring side of the bearing (200).

33. The fluid machine of claim 32, wherein the radial suction holes (220) terminate in a first suction communication port (2201), the suction channels (56) terminate in a second suction communication port (561),

when the sliding block (40) at the cylinder sleeve (20) is at an air inlet position, the first air inlet communication port (2201) is communicated with the corresponding variable-volume cavity (311), and when the sliding block (40) at the cylinder sleeve (20) is at an air outlet position, the corresponding variable-volume cavity (311) is communicated with the compression air outlet (22);

when the sliding block (40) at the bearing (200) is at an air inlet position, the second air inlet communication port (561) is communicated with the corresponding variable-volume cavity (311), and when the sliding block (40) at the bearing (200) is at an air outlet position, the corresponding variable-volume cavity (311) is communicated with the flange air outlet (57).

34. The fluid machine of claim 33, wherein the fluid machine is a compressor.

35. The fluid machine of claim 32, wherein the radial suction holes (220) terminate in a first inlet communication port, the suction channels (56) terminate in a second inlet communication port,

when the sliding block (40) at the cylinder sleeve (20) is at an air inlet position, the compression exhaust port (22) is communicated with the corresponding variable-volume cavity (311), and when the sliding block (40) at the cylinder sleeve (20) is at an air outlet position, the corresponding variable-volume cavity (311) is communicated with the first air inlet communication port;

when the sliding block (40) at the bearing (200) is at an air inlet position, the flange air outlet (57) is communicated with the corresponding variable-volume cavity (311), and when the sliding block (40) at the bearing (200) is at an air outlet position, the corresponding variable-volume cavity (311) is communicated with the second air inlet communication port.

36. The fluid machine of claim 35, wherein the fluid machine is an expander.

37. A fluid machine as claimed in claim 2, wherein,

when the bearings (200) are arranged at the two ends of the axial end part of the cylinder sleeve (20), the cylinder sleeve (20) is provided with radial air suction holes (220) and axial diversion holes (230) communicated with the radial air suction holes (220);

Wherein one end of the axial flow dividing hole (230) is communicated with one of the two limiting channels (31), and the other end of the axial flow dividing hole (230) is communicated with the other of the two limiting channels (31).

38. The fluid machine according to claim 37, wherein the inner wall surface of the cylinder liner (20) has a suction chamber (23), the suction chamber (23) being in communication with the axial flow diversion hole (230).

39. The fluid machine according to claim 38, wherein the suction chamber (23) extends a first predetermined distance around the circumference of the inner wall surface of the cylinder liner (20) to form an arc-shaped suction chamber (23).

40. The fluid machine according to claim 38, wherein the number of the air suction cavities (23) is two, the two air suction cavities (23) are arranged at intervals along the axial direction of the cylinder sleeve (20), and the two air suction cavities (23) are in one-to-one correspondence and are communicated with the two limit channels (31).

41. The fluid machine of claim 38, wherein the cylinder liner (20) has a compression exhaust port (22) and the radial suction hole (220) have a phase difference therebetween.

42. The fluid machine according to claim 41, wherein the number of the compression exhaust ports (22) is two, the two compression exhaust ports (22) are arranged at intervals along the axial direction of the cylinder sleeve (20), and the two compression exhaust ports (22) are in one-to-one correspondence and are communicated with the two limiting channels (31).

43. The fluid machine according to claim 42, wherein the suction chamber (23) terminates in an inlet communication port,

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 compression exhaust port (22).

44. The fluid machine of claim 43, wherein the fluid machine is a compressor.

45. The fluid machine according to claim 42, wherein the suction chamber (23) terminates in an inlet communication port,

when any sliding block (40) is at an air inlet position, the compression air outlet (22) 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.

46. The fluid machine of claim 45, wherein the fluid machine is an expander.

47. A heat exchange device comprising a fluid machine, characterized in that the fluid machine is a fluid machine as claimed in any one of claims 1 to 46.