CN116241467A

CN116241467A - Fluid machine and heat exchange device with bearing

Info

Publication number: CN116241467A
Application number: CN202111487193.4A
Authority: CN
Inventors: 杜忠诚; 李直; 张培林; 于瑞波; 宋雪威; 杨春霞; 姜秋来
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; the bearing is arranged in the cylinder sleeve and is positioned at the axial end part of 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, 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 is positioned at the axial end part of 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 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, an annular sinking groove is formed in the axial end face of the cylinder sleeve, the distance of the groove bottom of the annular sinking groove extending inwards along the radial direction of the cylinder sleeve is equal to the distance between the inner ring and the outer ring of the bearing, and the bearing is arranged at the annular sinking groove.

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 Q of the outer peripheral surface of the intersecting groove structure and the height N of the bearing satisfy: Q/N is more than or equal to 3 and less than or equal to 7.

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 0.005-0.08 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, 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 diameter R of the outer peripheral surface of the intersecting groove structure and the height N of the bearing satisfy: R/N is more than or equal to 1.5 and less than or equal to 3.5.

Further, the cylinder sleeve is provided with a compression air inlet and a compression air outlet, and when any sliding block is positioned at the air inlet position, the compression air inlet 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 inner wall surface of the cylinder sleeve is provided with an air suction cavity which is communicated with the compression air inlet.

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 two air suction cavities are arranged at intervals along the axial direction of the cylinder sleeve, the cylinder sleeve is further provided with an air suction communication cavity, the two air suction cavities are communicated with the air suction communication cavity, and the compression air inlet is communicated with the air suction cavity through the air suction communication cavity.

Further, the air suction communication cavity extends along the axial direction of the cylinder sleeve for a second preset distance.

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

Further, 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 machine further comprises an exhaust valve assembly which is arranged in the exhaust cavity and corresponds to the compression exhaust port.

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, the exhaust valve assemblies are two groups, and the two groups of exhaust valve assemblies are respectively arranged corresponding to the two compression exhaust ports.

Further, the axial end face of the cylinder sleeve is also provided with a communication hole, the communication hole is communicated with the exhaust cavity, the fluid machine further comprises a flange, an exhaust channel is arranged on the flange, and the communication hole is communicated with the exhaust channel.

Further, the exhaust cavity penetrates through the outer wall surface of the cylinder sleeve, and the fluid machine further comprises an exhaust cover plate which is connected with the cylinder sleeve and seals the exhaust cavity.

Further, the fluid machine is a compressor.

Further, the cylinder sleeve is provided with an expansion exhaust port and an expansion air inlet, and when any sliding block is positioned at the air inlet position, the expansion exhaust port is communicated with the corresponding volume cavity; when any sliding block is at the exhaust position, the corresponding volume cavity is communicated with the expansion air inlet.

Further, the inner wall surface of the cylinder sleeve is provided with an expansion exhaust cavity, and the expansion exhaust cavity is communicated with the expansion exhaust port.

Further, the expansion exhaust chamber extends around the circumferential direction of the inner wall surface of the cylinder by a first preset distance to form an arc-shaped expansion exhaust chamber, and the expansion exhaust chamber extends from the expansion exhaust port to the side where the expansion air inlet is located, and the extending direction of the expansion exhaust chamber is in the same direction as the rotating direction of the cross groove structure.

Further, the two expansion exhaust chambers are arranged at intervals along the axial direction of the cylinder sleeve, the cylinder sleeve is further provided with expansion exhaust communication chambers, the two expansion exhaust chambers are communicated with the expansion exhaust communication chambers, and the expansion exhaust ports are communicated with the expansion exhaust chambers through the expansion exhaust communication chambers.

Further, the expansion exhaust communication cavity extends for a second preset distance along the axial direction of the cylinder sleeve, and at least one end of the expansion exhaust communication cavity penetrates through the axial end face of the cylinder sleeve.

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 the driving torque of the other eccentric part of the two eccentric parts drives the corresponding sliding block to be the maximum value at the moment, the eccentric part with the maximum driving torque can normally drive the corresponding sliding block to rotate, thereby driving the cross groove structure to rotate through the sliding block, further driving the sliding block at the dead point position to continuously rotate through the cross groove structure, realizing the stable operation of the fluid machinery, avoiding the dead point position of the moving mechanism, improving the moving reliability of the fluid machinery, namely, ensuring the higher energy efficiency and lower noise of the compressor, and ensuring the working reliability of heat exchange equipment.

In addition, through setting up at least one bearing in the cylinder liner and being located the axial tip department of cylinder liner, and the outer lane of bearing is laminated with the inner wall of cylinder liner, like this, the outer peripheral face of cross groove structure passes through the bearing and supports antifriction for change the rolling friction of cross groove structure's circumference outer surface and bearing from sliding friction between cross groove structure's the circumference outer surface with the inner wall of cylinder liner, reduced mechanical friction consumption, wherein, the inner circle of bearing cooperates with cross groove structure, the inner circle of bearing cooperates with the inner wall of cylinder liner.

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

FIG. 5 shows a schematic view of the pump body assembly of FIG. 4 with bearings at both axial ends of the cross slot structure;

FIG. 6 shows a schematic view of the structure of the cross-grooved structure of FIG. 4 with an alternative embodiment bearing at both axial ends;

FIG. 7 shows an exploded view of the pump body assembly of FIG. 4;

FIG. 8 shows a schematic diagram of the assembled structure of the crankshaft, cross slot structure, and slider of FIG. 7;

FIG. 9 shows a schematic cross-sectional view of the crankshaft, cross slot configuration, and slider of FIG. 8;

FIG. 10 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. 7;

FIG. 11 is a schematic cross-sectional structural view showing the amount of assembly eccentricity of the crankshaft and cylinder liner of FIG. 7;

FIG. 12 shows a schematic view of the cylinder liner and lower flange of FIG. 7 in an exploded condition;

FIG. 13 is a schematic view showing the structure of the eccentricity between the cylinder liner and the lower flange of FIG. 12;

FIG. 14 shows a schematic view of the slider of FIG. 7 in the axial direction of the through hole;

FIG. 15 shows a schematic structural view of the cylinder liner of FIG. 7;

FIG. 16 shows a schematic cross-sectional structural view of the cylinder liner of FIG. 15, with the exhaust cover plate omitted;

FIG. 17 shows a schematic view of the structure of the Y-direction view in FIG. 16;

FIG. 18 shows a schematic cross-sectional structural view of the cylinder liner and lower flange of FIG. 4, illustrating the suction path of the pump body assembly;

FIG. 19 shows a schematic structural view of the cylinder liner of FIG. 18;

FIG. 20 shows a schematic cross-sectional structural view of the cylinder liner of FIG. 19;

FIG. 21 shows a schematic cross-sectional structural view of the cylinder liner of FIG. 19 from another perspective;

FIG. 22 shows a schematic cross-sectional structural view of another view of the pump body assembly of FIG. 4;

FIG. 23 shows a schematic structural view of the upper flange of FIG. 22;

FIG. 24 shows a schematic view of the lower flange of FIG. 22;

FIG. 25 is a schematic view showing a state structure of the compressor of FIG. 3 at the start of suction;

FIG. 26 is a schematic view showing a state structure of the compressor of FIG. 3 during suction;

FIG. 27 is a schematic view showing a state structure of the compressor of FIG. 3 at the end of suction;

FIG. 28 is a schematic view showing a state structure of the compressor of FIG. 3 when compressed gas is supplied;

FIG. 29 is a schematic view showing a state structure of the compressor of FIG. 3 in a discharge process;

FIG. 30 is a schematic view showing a state structure of the compressor of FIG. 3 at the end of discharge;

FIG. 31 shows a schematic view of the structure of the cross-grooved structure of FIG. 4 with an alternative embodiment bearing at both axial ends;

fig. 32 is a schematic view showing an internal structure of a compressor according to a second embodiment of the present invention;

FIG. 33 shows a schematic view of the pump body assembly of the compressor of FIG. 32;

fig. 34 is a schematic view showing an internal structure of a compressor according to a third embodiment of the present invention;

FIG. 35 shows a schematic structural view of a pump body assembly of the compressor of FIG. 34;

FIG. 36 shows a schematic view of a cross slot configuration and slider configuration in accordance with an alternative embodiment of the present invention;

FIG. 37 shows a schematic view of a cross slot configuration and slider configuration in accordance with an alternative embodiment of the present invention;

FIG. 38 shows a schematic view of a cross slot configuration and slider configuration in accordance with an alternative embodiment of the present invention;

FIG. 39 shows a schematic diagram of a cross slot configuration and slider configuration in accordance with an alternative embodiment of the present invention;

FIG. 40 is a schematic diagram illustrating the mechanism of operation of a prior art compressor;

FIG. 41 is a schematic diagram showing the mechanism principle of operation of the compressor modified in the prior art;

FIG. 42 is a schematic diagram of the mechanism of operation of the compressor of FIG. 41 showing the moment arm of the drive shaft driving the slider in rotation;

fig. 43 shows a schematic view of the principle of the mechanism of operation of the compressor of fig. 41, 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; 21. a compression intake; 22. a compression exhaust port; 23. an air suction cavity; 24. an air suction communication cavity; 25. an exhaust chamber; 26. a communication hole; 210. an annular sinking groove;

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;

60. an exhaust valve assembly; 61. an exhaust valve plate; 62. a valve plate baffle;

70. an exhaust cover plate;

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. 40, 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. 41, 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 provided, which 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 cylinderCoaxially arranged with the spacing groove structure, i.e. the cylinder centre 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. 42, 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. 43, 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 is arranged in the cylinder sleeve 20 and positioned at the axial end part of 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 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, and 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 stable operation of the fluid machinery is realized, the dead point position of the moving mechanism is avoided, the movement reliability of the fluid machinery is improved, namely, the efficiency of the compressor is ensured, the noise is lower, and the heat exchange equipment is ensured.

In addition, by providing at least one bearing 200 inside the cylinder liner 20 at an end portion in the axial direction of the cylinder liner 20, and the outer ring of the bearing 200 is fitted with the inner wall of the cylinder liner 20, in this way, the outer circumferential surface of the cross groove structure 30 is supported by the bearing 200 to reduce friction, so that sliding friction between the circumferential outer surface of the cross groove structure 30 and the inner wall of the cylinder liner 20 is changed into rolling friction between the circumferential outer surface of the cross groove structure 30 and the bearing 200, mechanical friction power consumption is reduced, wherein the inner ring of the bearing 200 is fitted with the cross groove structure 30, and the inner ring of the bearing 200 is fitted with the inner wall of the cylinder liner 20.

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 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 Two limiting channels 31 of the cross slot structure 30 are respectively used as the firstThree-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 Is equal in length, so that,while the crankshaft 10 rotates, the eccentric portion 11 of the crankshaft 10 drives the corresponding slide block 40 to rotate around the axis O of the crankshaft 10 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 31, in the present embodiment, both ends of the cylinder liner 20 in the axial direction have bearings 200. In this way, rotational smoothness of the cross groove structure 30 within the cylinder liner 20 is ensured.

As shown in fig. 7 and 19, an annular countersink 210 is provided at an axial end surface of the cylinder liner 20, a groove bottom of the annular countersink 210 extends radially inward of the cylinder liner 20 by a distance equal to a distance between inner and outer rings of the bearing 200, and the bearing 200 is mounted at the annular countersink 210. In this way, the bearing 200 is installed in the cylinder sleeve 20 in an embedded manner, so that not only can the inclination of the cross groove structure 30 be effectively prevented, but also the mechanical friction can be reduced, the height of each part of the pump body assembly 83 can be kept unchanged, and the mass production is facilitated.

As shown in fig. 6, the diameter Q of the outer peripheral surface of the intersecting groove structure 30 and the height N of the bearing 200 satisfy: Q/N is more than or equal to 3 and less than or equal to 7. The diameter R of the outer peripheral surface of the intersecting groove structure 30 and the height N of the bearing 200 satisfy: R/N is more than or equal to 1.5 and less than or equal to 3.5. Thus, the cross groove structure 30 is effectively prevented from tilting, and good lubrication between the cross groove structure 30 and the cylinder sleeve 20 is ensured, so that mechanical friction power consumption between the cross groove structure 30 and the cylinder sleeve 20 is reduced, the performance of the compressor is improved, and the running reliability of the compressor is improved.

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 31, 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. 10, the eccentric amounts of the two eccentric portions 11 are equal to e, as shown in fig. 11, 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. 13, 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.

As shown in fig. 7, 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. 4, 7 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. 4, 7 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 0.08mm.

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. 4, 7 to 11, 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 and 7 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. 7, 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. 14, 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. 14, 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. 14 indicates the circle in which the centers of the two cambered surfaces are located.

In the present application, as shown in fig. 7, 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 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. 25 to 30, the slider 40 rotates relative to the cylinder liner 20 while reciprocating in the limiting passage 31, in fig. 25 to 27, 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 23 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 is separated from the suction chamber 23 at this time, thereby completing the suction operation, in fig. 28 to 30, the variable volume chamber 311 decreases in the process of continuing to rotate the slider 40 clockwise from 180 degrees to 360 degrees, the slider 40 compresses the gas in the variable volume chamber 311, when the slider 40 rotates to 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 61 of the exhaust valve assembly 60 opens, and the exhaust operation starts until the next cycle is entered after the compression is completed.

As shown in fig. 25 to 30, the point marked with M is used as a reference point for the relative movement of the slide 40 and the crankshaft 10, fig. 26 shows a clockwise rotation of the slide 40 from 0 degrees to 180 degrees, the slide 40 rotates at an angle θ1, the corresponding crankshaft 10 rotates at an angle 2θ1, fig. 28 shows a continued clockwise rotation of the slide 40 from 180 degrees to 360 degrees, the slide 40 rotates at an angle 180 ° +θ2, the corresponding crankshaft 10 rotates at an angle 360 ° +2θ2, fig. 29 shows a continued clockwise rotation of the slide 40 from 180 degrees to 360 degrees, and the variable volume chamber 311 communicates with the compression exhaust port 22, the slide 40 rotates at an angle 180 ° +θ3, the corresponding crankshaft 10 rotates at an angle 360 ° +2θ3, that is, the slide 40 rotates 1 turn, the corresponding crankshaft 10 rotates 2 turns, and θ1 < θ2 < θ3.

Specifically, as shown in fig. 12, 15 to 21, and 25 to 30, the cylinder liner 20 has a compression intake port 21 and a compression exhaust port 22, and when any one of the sliders 40 is in the intake position, the compression intake port 21 is in communication 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.

As shown in fig. 12, 15 to 21, and 25 to 30, the inner wall surface of the cylinder liner 20 has a suction chamber 23, and the suction chamber 23 communicates with the compression intake 21. 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. 15, 16 and 18, the number of the air suction chambers 23 is two, the two air suction chambers 23 are arranged at intervals along the axial direction of the cylinder sleeve 20, the cylinder sleeve 20 is also provided with an air suction communication chamber 24, the two air suction chambers 23 are communicated with the air suction communication chamber 24, and the compression air inlet 21 is communicated with the air suction chamber 23 through the air suction communication chamber 24. In this way, it is advantageous to increase the volume of the suction chamber 23, thereby reducing suction pressure pulsation.

As shown in fig. 15, 16 and 18, the suction communication chamber 24 extends a second preset distance in the axial direction of the cylinder liner 20.

As shown in fig. 19 to 21, in another embodiment of the cylinder liner 20, two air suction chambers 23 are provided, the two air suction chambers 23 are arranged at intervals along the axial direction of the cylinder liner 20, two compression air inlets 21 are provided, and the two compression air inlets 21 are arranged in one-to-one correspondence with and are communicated with the two air suction chambers 23. In this way, it is advantageous to increase the volume of the suction chamber 23, thereby reducing suction pressure pulsation.

As shown in fig. 12, 15-21 and 25-30, the outer wall of the cylinder sleeve 20 is provided with an exhaust cavity 25, the compression exhaust port 22 is communicated to the exhaust cavity 25 from the inner wall of the cylinder sleeve 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. In this way, the exhaust cavity 25 is used for accommodating the exhaust valve assembly 60, so that the occupied space of the exhaust valve assembly 60 is effectively reduced, components are reasonably arranged, and the space utilization rate of the cylinder sleeve 20 is improved.

As shown in fig. 16, 17 and 19, there are two compression exhaust ports 22, two compression exhaust ports 22 are arranged at intervals along the axial direction of the cylinder liner 20, two exhaust valve assemblies 60 are arranged in two groups, and two groups of exhaust valve assemblies 60 are respectively arranged corresponding to the two compression exhaust ports 22. In this way, since the two compression exhaust ports 22 are respectively provided with the two groups of exhaust valve assemblies 60, a great amount of gas in the variable volume cavity 311 is effectively prevented from leaking, and the compression efficiency of the variable volume cavity 311 is ensured.

As shown in fig. 16, the exhaust valve assembly 60 is connected with the cylinder liner 20 through a fastener 90, the exhaust valve assembly 60 includes an exhaust valve plate 61 and a valve plate baffle 62, the exhaust valve plate 61 is disposed in the exhaust chamber 25 and shields the corresponding compression exhaust port 22, and the valve plate baffle 62 is disposed on the exhaust valve plate 61 in an overlapping manner. In this way, the valve block baffle 62 effectively avoids the transition opening of the exhaust valve block 61, thereby ensuring the exhaust performance of the cylinder sleeve 20.

Alternatively, the fastener 90 is a screw.

As shown in fig. 12 and 15, the axial end surface of the cylinder liner 20 is further provided with a communication hole 26, the communication hole 26 communicates with the exhaust chamber 25, the fluid machine further includes a flange 50, an exhaust passage 51 is provided on the flange 50, and the communication hole 26 communicates with the exhaust passage 51. In this way, the exhaust reliability of the cylinder liner 20 is ensured.

As shown in fig. 15, the exhaust chamber 25 penetrates through the outer wall surface of the cylinder liner 20, and the fluid machine further includes an exhaust cover plate 70, and the exhaust cover plate 70 is connected to the cylinder liner 20 and seals the exhaust chamber 25. In this way, the vent cover plate 70 functions to isolate the variable volume chamber 311 from the external space of the pump body assembly 83.

As shown in fig. 18 and 19, when the pressure of the variable volume chamber 311 reaches the discharge pressure after the variable volume chamber 311 is communicated with the compression discharge port 22, the discharge valve plate 61 is opened, and the compressed gas enters the discharge chamber 25 through the compression discharge port 22, passes through the communication hole 26 on the cylinder liner 20, is discharged through the discharge passage 51 and enters the external space of the pump body assembly 83 (i.e., the cavity of the compressor), thereby completing the discharge process.

Optionally, the exhaust cover plate 70 is secured to the cylinder liner 20 by fasteners 90.

Alternatively, the fastener 90 is a screw.

Optionally, the outer contour of the vent flap 70 is adapted to the outer contour of the vent chamber 25.

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 cylinder sleeve 20 is provided with an expansion exhaust port and an expansion air inlet, and when any slide block 40 is positioned at the air inlet position, the expansion exhaust port is communicated with the corresponding volume cavity 311; when any one of the sliders 40 is in the exhaust position, the corresponding volume chamber 311 is in communication with the expansion intake port.

Optionally, the inner wall surface of the cylinder liner 20 has an expansion exhaust chamber in communication with the expansion exhaust port.

Further, the expansion exhaust chamber extends around the circumferential direction of the inner wall surface of the cylinder by a first preset distance to form an arc-shaped expansion exhaust chamber, and the expansion exhaust chamber extends from the expansion exhaust port to the side where the expansion air inlet is located, and the extending direction of the expansion exhaust chamber is in the same direction as the rotating direction of the cross groove structure 30.

Further, two expansion exhaust chambers are arranged at intervals along the axial direction of the cylinder sleeve 20, the cylinder sleeve 20 is further provided with expansion exhaust communication chambers, the two expansion exhaust chambers are communicated with the expansion exhaust communication chambers, and the expansion exhaust ports are communicated with the expansion exhaust chambers through the expansion exhaust communication chambers.

Further, the expansion exhaust communication chamber extends a second preset distance along the axial direction of the cylinder liner 20, and at least one end of the expansion exhaust communication chamber penetrates through the axial end surface of the cylinder liner 20.

Example two

As shown in fig. 32 and 33, the present embodiment differs from the first embodiment in that only one end of the axial end portion of the cylinder liner 20 is provided with the bearing 200, that is, the lower side of the intersecting groove structure 30 has the bearing 200.

In the present embodiment, since the bearing 200 is located at one end of the axial end portion of the cylinder liner 20, the intake and exhaust of the cylinder liner 20 in the first embodiment are still applicable.

Example III

As shown in fig. 34 and 35, the present embodiment differs from the second embodiment in that only one end of the axial end portion of the cylinder liner 20 is provided with a bearing 200, that is, the upper side of the intersecting groove structure 30 has the bearing 200.

As shown in fig. 36 to 39, the projection of the slider 40 in the sliding direction is adapted to the cross section of the limiting channel 31, wherein fig. 36 is a direction slider chamfer and a corresponding cross groove structure 30, fig. 37 is a trapezoidal slider and a corresponding cross groove structure 30, fig. 38 is a trapezoidal slider chamfer and a corresponding cross groove structure 30, and fig. 39 is a semicircle+straight-edge 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 at least one, the bearing (200) is arranged in the cylinder sleeve (20) and is positioned at the axial end part of 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 circumferential surface 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. The fluid machine according to claim 1, characterized in that an annular countersink (210) is provided at an axial end face of the cylinder liner (20), a groove bottom of the annular countersink (210) extends radially inwards along the cylinder liner (20) by a distance equal to a distance between an inner and an outer ring of the bearing (200), the bearing (200) being mounted at the annular countersink (210).

3. 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).

4. The fluid machine according to claim 1, characterized in that the diameter Q of the outer peripheral surface of the cross groove structure (30) and the height N of the bearing (200) satisfy between: Q/N is more than or equal to 3 and less than or equal to 7.

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 peripheral 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 0.08mm.

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).

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 (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).

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 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).

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. The fluid machine according to claim 1, characterized in that the diameter R of the outer peripheral surface of the cross groove structure (30) and the height N of the bearing (200) satisfy between: R/N is more than or equal to 1.5 and less than or equal to 3.5.

29. The fluid machine according to claim 1, wherein the cylinder liner (20) has a compression intake (21) and a compression exhaust (22),

when any sliding block (40) is at an air inlet position, the compression air inlet (21) 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).

30. The fluid machine according to claim 29, characterized in that the inner wall surface of the cylinder liner (20) has a suction chamber (23), the suction chamber (23) being in communication with the compression intake (21).

31. The fluid machine according to claim 30, 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).

32. The fluid machine according to claim 30, wherein the number of the suction chambers (23) is two, the two suction chambers (23) are arranged at intervals along the axial direction of the cylinder sleeve (20), the cylinder sleeve (20) is further provided with a suction communication chamber (24), the two suction chambers (23) are communicated with the suction communication chamber (24), and the compression air inlet (21) is communicated with the suction chamber (23) through the suction communication chamber (24).

33. The fluid machine according to claim 32, wherein the suction communication chamber (24) extends a second predetermined distance in the axial direction of the cylinder liner (20).

34. The fluid machine according to claim 30, wherein the number of the suction chambers (23) is two, the two suction chambers (23) are arranged at intervals along the axial direction of the cylinder sleeve (20), the number of the compression air inlets (21) is two, and the two compression air inlets (21) are arranged in one-to-one correspondence with and are communicated with the two suction chambers (23).

35. The fluid machine of claim 29, wherein the outer wall of the cylinder sleeve (20) is provided with an exhaust cavity (25), the compression exhaust port (22) is communicated to the exhaust cavity (25) by the inner wall of the cylinder sleeve (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).

36. The fluid machine of claim 35, wherein there are two compression exhaust ports (22), the two compression exhaust ports (22) are disposed at intervals along the axial direction of the cylinder liner (20), the exhaust valve assemblies (60) are in two groups, and the two groups of exhaust valve assemblies (60) are disposed corresponding to the two compression exhaust ports (22), respectively.

37. The fluid machine according to claim 36, characterized in that a communication hole (26) is further provided on an axial end face of the cylinder liner (20), the communication hole (26) being in communication with the exhaust chamber (25), the fluid machine further comprising a flange (50), an exhaust passage (51) being provided on the flange (50), the communication hole (26) being in communication with the exhaust passage (51).

38. The fluid machine according to claim 35, characterized in that the exhaust chamber (25) penetrates to the outer wall surface of the cylinder liner (20), the fluid machine further comprising an exhaust cover plate (70), the exhaust cover plate (70) being connected to the cylinder liner (20) and sealing the exhaust chamber (25).

39. A fluid machine as claimed in any one of claims 29 to 38, wherein the fluid machine is a compressor.

40. The fluid machine according to claim 1, wherein the cylinder liner (20) has an expansion exhaust port and an expansion intake port,

when any sliding block (40) is at an air inlet position, the expansion exhaust 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 expansion air inlet.

41. The fluid machine of claim 40, wherein the inner wall surface of the cylinder liner (20) has an expansion exhaust chamber, the expansion exhaust chamber being in communication with the expansion exhaust port.

42. The fluid machine according to claim 41, wherein the expansion exhaust chamber extends a first predetermined distance around the circumferential direction of the inner wall surface of the cylinder liner (20) to constitute an arc-shaped expansion exhaust chamber, and the expansion exhaust chamber extends from the expansion exhaust port to the side where the expansion intake port is located, the direction of extension of the expansion exhaust chamber being in the same direction as the direction of rotation of the intersecting groove structure (30).

43. The fluid machine of claim 42, wherein there are two expansion exhaust chambers, the two expansion exhaust chambers being disposed at intervals along an axial direction of the cylinder liner (20), the cylinder liner (20) further having an expansion exhaust communication chamber, both of the expansion exhaust chambers being in communication with the expansion exhaust communication chamber, and the expansion exhaust port being in communication with the expansion exhaust chamber through the expansion exhaust communication chamber.

44. The fluid machine of claim 43, wherein said expansion exhaust communication chamber extends a second predetermined distance in an axial direction of said cylinder liner (20), at least one end of said expansion exhaust communication chamber penetrating an axial end face of said cylinder liner (20).

45. The fluid machine of any one of claims 40 to 44, wherein the fluid machine is an expander.

46. 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 45.