CN117145773A

CN117145773A - Fluid machine and heat exchange device

Info

Publication number: CN117145773A
Application number: CN202210568373.3A
Authority: CN
Inventors: 任丽萍; 杜忠诚; 于瑞波; 李直; 张培林
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2022-05-23
Filing date: 2022-05-23
Publication date: 2023-12-01
Also published as: WO2023226414A1

Abstract

The invention provides a fluid machine and heat exchange equipment, wherein the fluid machine comprises a crankshaft, a cylinder sleeve, a cross groove structure, a sliding block and two flanges, 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 cross groove structure is rotatably arranged in the cylinder sleeve, two limiting channels of the cross 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 two eccentric parts correspondingly extend into the two through holes of the two sliding blocks; at least one of the two flanges is provided with an exhaust channel; the side wall surface of the cylinder sleeve is provided with two exhaust ports which are arranged at intervals along the axial direction of the cylinder sleeve and are communicated with the exhaust channel; the cross-sectional area of the hole section of the exhaust port is S1, and the volume of the single variable volume cavity is V1, wherein, the ratio of V1 to S1 is more than or equal to 750 and is less than or equal to 3300. The invention solves the problems of low energy efficiency, high noise and low exhaust loss of the compressor in the prior art.

Description

Fluid machine and heat exchange device

Technical Field

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

Background

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

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

In addition, the existing partial compressors have poor efficiency due to a large loss of exhaust gas.

Disclosure of Invention

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

In order to achieve the above object, according to one aspect of the present invention, there is provided a fluid machine including a crankshaft, a cylinder liner, a cross groove structure, a slider, and two flanges, the crankshaft being 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 cross groove structure is rotatably arranged in the cylinder sleeve and 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 blocks are provided with through holes, 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 way to form a variable-volume cavity, the variable-volume cavity is positioned in the sliding direction of the sliding blocks, and the crankshaft rotates to drive the sliding blocks to reciprocally slide in the limiting channels and interact with the cross groove structure, so that the cross groove structure and the sliding blocks rotate in the cylinder sleeve; the two flanges are respectively arranged at two axial ends of the cylinder sleeve, and at least one of the two flanges is provided with an exhaust channel; the side wall surface of the cylinder sleeve is provided with two exhaust ports which are arranged at intervals along the axial direction of the cylinder sleeve and are communicated with the exhaust channel; the cross-sectional area of the hole section of the exhaust port is S1, and the volume of the single variable volume cavity is V1, wherein, the ratio of V1 to S1 is more than or equal to 750 and is less than or equal to 3300.

Further, the positions of the two exhaust ports in the circumferential direction of the cylinder liner are identical.

Further, the projection of the sliding block in the axial direction of the through hole is provided with two relatively parallel straight line sections and an arc line section connecting the end parts of the two straight line sections; the arrangement position of the exhaust port in the circumferential direction of the cylinder sleeve is in an angle range of (arccos (2R/B) to 2 x arccos (2R/B)), wherein R is the inner circle radius of the cylinder sleeve, and B is the distance between two relatively parallel straight line segments of the projection of the sliding block in the axial direction of the through hole.

Further, an exhaust cavity is formed in the outer wall of the cylinder sleeve, the exhaust port is communicated to the exhaust cavity through the inner wall of the cylinder sleeve, the fluid machine further comprises an exhaust valve assembly, the exhaust valve assembly is arranged in the exhaust cavity and corresponds to the exhaust port, the exhaust valve assembly is in two groups, and the two groups of exhaust valve assemblies are respectively corresponding to the two exhaust ports.

Further, a communication hole is further formed in the axial end face of the cylinder sleeve, the communication hole is communicated with the exhaust cavity, and the communication hole is communicated with the exhaust channel.

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

Further, the two exhaust chambers are communicated through an exhaust communication hole extending in the axial direction of the cylinder liner.

Further, the distance between the plane where the end of the exhaust port, which is communicated with the exhaust cavity, is K and the axis of the cylinder sleeve, and the inner circle radius of the cylinder sleeve is R, wherein K-R is less than or equal to 1mm and less than or equal to 5mm.

Further, the cross section area of the exhaust cavity in the axial direction of the cylinder sleeve is S2, the height of the single exhaust cavity in the axial direction of the cylinder sleeve is M, and the displacement of the fluid machine is V, wherein 0.5-V-5 is smaller than or equal to 5.

Further, an exhaust cavity is formed in the outer wall of the cylinder sleeve, a boss structure is arranged on the cavity wall surface of the exhaust cavity, and the exhaust port penetrates through the boss structure from the inner wall of the cylinder sleeve and is communicated with the exhaust cavity.

Further, the thickness of the boss structure in the extending direction of the exhaust port is N, wherein N is less than or equal to 0.05mm and less than or equal to 3mm.

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, 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.

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 applying the technical scheme of the application, at least one of the two flanges is provided with an exhaust channel; meanwhile, two exhaust ports are arranged on the side wall surface of the cylinder sleeve, are arranged at intervals along the axial direction of the cylinder sleeve, and are communicated with the exhaust channel; in addition, the cross section area of the hole section of the exhaust port is S1, and the volume of the single variable-volume cavity is V1, wherein, the volume is more than or equal to 750 and less than or equal to V1/S1 and less than or equal to 3300, so that the exhaust reliability of the fluid machinery is ensured, the exhaust loss of the fluid machinery is reduced, and the efficiency of the fluid machinery is improved.

Drawings

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

fig. 1 illustrates an internal structure of a compressor according to a first embodiment of the present application;

FIG. 2 shows a schematic structural view of a pump body assembly of the compressor of FIG. 1;

FIG. 3 shows an exploded view of the pump body assembly of FIG. 2;

FIG. 4 shows a schematic diagram of the assembled structure of the crankshaft, cross slot structure, and slider of FIG. 3;

FIG. 5 shows a schematic cross-sectional view of the crankshaft, cross slot configuration, and slider of FIG. 4;

FIG. 6 shows a schematic structural view of the shaft body portion and the eccentric amounts of the two eccentric portions of the crankshaft of FIG. 4;

FIG. 7 is a schematic cross-sectional structural view showing the amount of assembly eccentricity of the crankshaft and cylinder liner of FIG. 3;

FIG. 8 is a schematic view showing the structure of the eccentricity between the cylinder liner and the lower flange in FIG. 3;

FIG. 9 shows a schematic view of the slider of FIG. 3 in the axial direction of the through hole;

FIG. 10 is a schematic view showing a state structure of the compressor of FIG. 3 at the start of suction;

FIG. 11 is a schematic view showing a state structure of the compressor of FIG. 3 during suction;

FIG. 12 is a schematic view showing a state structure of the compressor of FIG. 3 at the end of suction;

FIG. 13 is a schematic view showing a state structure of the compressor of FIG. 3 when compressed gas is supplied;

FIG. 14 is a schematic view showing a state structure of the compressor of FIG. 3 in a discharge process;

FIG. 15 shows a schematic view of the compressor of FIG. 3 in a state at the end of discharge;

FIG. 16 shows a schematic structural view of the cylinder liner of FIG. 3;

FIG. 17 shows a schematic cross-sectional structural view of the cylinder liner of FIG. 3, showing the angular range of the exhaust ports disposed in the circumferential direction of the cylinder liner;

FIG. 18 shows a schematic cross-sectional structure of the cylinder liner of FIG. 3, showing K in relation to R;

FIG. 19 shows a schematic cross-sectional structural view of the pump body assembly of FIG. 2 from another perspective, showing an assembly eccentricity e between the crankshaft and cylinder liner;

FIG. 20 shows a schematic cross-sectional structural view of the cylinder liner of FIG. 2, with the cross-slot structure, the slide blocks, and the crankshaft omitted;

FIG. 21 shows a schematic view of the exhaust chamber side of the cylinder liner of FIG. 3;

FIG. 22 shows a schematic view of the exhaust chamber side of a cylinder liner with boss structures at the exhaust ports in accordance with an alternative embodiment of the present invention;

FIG. 23 shows a schematic view of the cylinder liner of FIG. 22 in partial cross-section;

FIG. 24 shows a schematic structural view of a cross section of the slider of FIG. 3 in its sliding direction;

fig. 25 shows a schematic structural view of a pump body assembly according to a second embodiment of the present invention;

fig. 26 shows a schematic structural view of a pump body assembly according to a third embodiment of the present invention;

FIG. 27 shows a schematic structural view of a pump body assembly according to a fourth embodiment of the present invention;

FIG. 28 illustrates a schematic mechanical diagram of the operation of a compressor in accordance with an alternative embodiment of the present invention;

FIG. 29 is a schematic diagram showing the principle of the mechanism of operation of the compressor of FIG. 28;

FIG. 30 is a schematic diagram illustrating the mechanism of operation of a prior art compressor;

FIG. 31 is a schematic diagram showing the mechanism principle of the compressor operation after improvement in the prior art;

FIG. 32 is a schematic diagram of the mechanism of operation of the compressor of FIG. 31 showing the moment arm of the drive shaft driving the slider in rotation;

FIG. 33 is a schematic view showing the principle of the mechanism of operation of the compressor of FIG. 31, wherein the center of the limit slot structure coincides with the center of the eccentric portion;

FIG. 34 shows a graphical representation of compressor discharge loss, COP, clearance volume versus V1/S1.

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. radial suction holes; 22. an exhaust port; 23. an air suction cavity; 24. an air suction communication cavity; 25. an exhaust chamber; 26. a communication hole; 28. an exhaust communication hole; 29. a boss structure;

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;

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. and a lower cover assembly.

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. 30, 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 segmentsO 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. 31, 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.

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. 32, 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. 33, 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 the principle, the application provides a brand-new mechanism principle of a cross groove structure with two limiting channels and double sliding blocks, and a brand-new compressor is constructed based on the principle, and the compressor has the characteristics of high energy efficiency and low noise.

In order to solve the problems of low energy efficiency and high noise of the compressor in the prior art, the application provides a fluid machine, a heat exchange device and an operation method of the fluid machine, wherein the heat exchange device comprises the fluid machine, and the fluid machine is operated by adopting the operation method.

The fluid machinery comprises a crankshaft 10, a cylinder sleeve 20, a cross groove structure 30 and a sliding block 40, wherein the crankshaft 10 is axially provided with two eccentric parts 11, a phase difference of a first included angle A is formed between the two eccentric parts 11, and the eccentric amounts of the two eccentric parts 11 are equal; the crankshaft 10 and the cylinder sleeve 20 are eccentrically arranged, and the eccentric distance is fixed; the cross groove structure 30 is rotatably arranged in the cylinder sleeve 20, 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, the extending direction of the limiting channels 31 is perpendicular to the axial direction of the crankshaft 10, and a phase difference of a second included angle B is arranged between the extending directions of the two limiting channels 31, wherein the first included angle A is twice the second included angle B; 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, simultaneously, the two sliding blocks 40 correspondingly slide in the two limiting channels 31 and form a variable volume cavity 311, as a first included angle A between the two eccentric parts 11 is twice as large as a second included angle B between extending directions of the two limiting channels 31, 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 corresponding sliding block 40 can be normally driven to rotate by the sliding block 40, the cross groove structure 30 is driven to rotate by the cross groove structure 30, the sliding block 40 at the dead point position is driven to continuously rotate by the cross groove structure 30, the reliability of the mechanical movement of the fluid is ensured, the mechanical movement is avoided, and the reliability of the mechanical movement is ensured, and the working reliability is ensured.

In addition, 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 lower, and therefore, the working reliability of the heat exchange equipment is ensured.

In the present application, the first angle a and the second angle B are not zero.

As shown in fig. 28 and 29, when the fluid machine described above is operated, the crankshaft 10 is wound around the axial center 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 them is equal to the corresponding second offset of the crankshaft 10The eccentric amount of the core 11 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 (see fig. 28).

As shown in fig. 29, 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. 29, 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 Revolution angular velocity and slip of (a)The rotational angular velocity of the block 40 with respect to the eccentric portion 11 is the same.

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

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

Example 1

As shown in fig. 1 to 24, 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, 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 the assembly eccentricity of the crankshaft 10 and the cylinder liner 20 by an essence of aligning of the flange 50.

Specifically, as shown in fig. 6, the eccentric amounts of the two eccentric portions 11 are equal to e, as shown in fig. 7, 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. 8, the distance between the inner ring axis of the cylinder liner 20 and the inner ring axis of the lower flange 53 is e, that is, equal to the eccentric amount of the eccentric portion 11.

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

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

Alternatively, the two sliders 40 are respectively arranged concentrically with the two eccentric portions 11, the sliders 40 do circular motion around the axis of the crankshaft 10, and a first rotation gap is formed between the 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.

Optionally, a second rotation gap is provided between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder liner 20, and the size of the second rotation gap is 0.005 mm-0.1 mm.

As shown in fig. 2 to 7, 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 of the present application, the shaft portion 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. 2 to 7, 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 of the present application, not shown, the shaft portion 12 of the crankshaft 10 is detachably connected to the eccentric portion 11. In this way, the installation and the removal of the eccentric portion 11 are facilitated.

As shown in fig. 3 and 4, 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.

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

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

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

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

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

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

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

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

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

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

As shown in fig. 2 to 7, 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 of 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. 2 to 7, 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. 3, 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. 9, 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. 9, 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. 9 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.

In the present application, the projected area S of the pressing surface 42 in the sliding direction of the slider 40 _{Sliding block} Area S of the compression exhaust port 22 with the cylinder liner 20 _{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. 1, 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 corresponding two 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. 2 and 3.

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.

Further, the closed space surrounded by the extrusion surface 42 of the head of the sliding block 40, the two side wall surfaces and the channel bottom surface of the limiting channel 31, the partial inner wall surface of the cylinder liner 20, and the partial surface of the upper flange 52 facing the cylinder liner 20 (or the partial surface of the lower flange 53 facing the cylinder liner 20) is the variable volume cavity 311.

As shown in fig. 10 to 15, the slider 40 rotates relative to the cylinder liner 20 while reciprocating in the limiting passage 31, in fig. 10 to 12, 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. 13 to 15, 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 of the exhaust valve assembly opens, and the exhaust operation starts until the next cycle is entered after the compression is completed.

As shown in fig. 10 to 15, with the point marked M as the reference point for the relative movement of the slide block 40 and the crankshaft 10, fig. 11 shows a process in which the slide block 40 rotates clockwise from 0 degrees to 180 degrees, the slide block 40 rotates at an angle θ1, the corresponding crankshaft 10 rotates at an angle 2θ1, fig. 13 shows a process in which the slide block 40 continues to rotate clockwise from 180 degrees to 360 degrees, the slide block 40 rotates at an angle 180 ° +θ2, the corresponding crankshaft 10 rotates at an angle 360 ° +2θ2, fig. 14 shows a process in which the slide block 40 continues to rotate clockwise from 180 degrees to 360 degrees, and the variable volume chamber 311 communicates with the compression exhaust port 22, the slide block 40 rotates at an angle 180 ° +θ3, and the corresponding crankshaft 10 rotates at an angle 360 ° +2θ3, that is, the slide block 40 rotates 1 turn, and the corresponding crankshaft 10 rotates 2 turns, where θ1 < θ2 < θ3.

The operation of the compressor is described in detail below:

as shown in fig. 1, 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.

Aiming at the problem of how to reduce the exhaust loss, the application reduces the exhaust loss of the compressor by exhausting the air at the side of the cylinder sleeve 20, and specifically comprises the following steps:

as shown in fig. 1 to 24 and 34, two flanges 50 are respectively arranged at two axial ends of the cylinder sleeve 20, and at least one flange 50 of the two flanges 50 is provided with an exhaust passage 51; wherein, two exhaust ports 22 are arranged on the side wall surface of the cylinder sleeve 20, the two exhaust ports 22 are arranged at intervals along the axial direction of the cylinder sleeve 20, and the two exhaust ports 22 are communicated with an exhaust passage 51; the cross-sectional area of the hole section of the exhaust port 22 is S1, and the volume of the single variable volume chamber 311 is V1, where 750+.V1/S1+.3300.

An exhaust passage 51 is formed in at least one flange 50 of the two flanges 50; meanwhile, two exhaust ports 22 are arranged on the side wall surface of the cylinder sleeve 20, the two exhaust ports 22 are arranged at intervals along the axial direction of the cylinder sleeve 20, and the two exhaust ports 22 are communicated with an exhaust channel 51; in addition, the cross-sectional area of the hole section of the exhaust port 22 is S1, and the volume of the single variable volume chamber 311 is V1, wherein 750+.v1/s1+.3300, so that the exhaust reliability of the fluid machine is ensured, thereby reducing the exhaust loss of the fluid machine and being beneficial to improving the efficiency of the fluid machine.

Further, the unit of S1 is square millimeter, and the unit of V1 is cubic millimeter.

In the present application, the value range of the ratio V1/S1 is the ratio of the numerical values, and the values are the same without units, and in addition, since the volume of the single variable volume chamber 311 is a variable value, the ratio range of V1 at the maximum in the present application is 750+.v1/s1+.3300.

As shown in fig. 34, COP refers to the performance of the compressor, i.e., the ratio of the output cooling capacity or heating capacity to the power consumed by the compressor.

In the present application, as shown in fig. 24, the cross section of the sliding block 40 in the sliding direction is S, and as shown in fig. 19, the fitting eccentricity of the cross groove structure 30 is e, and it can be obtained according to the compressor operation principle: the volume v1=4es of the single variable volume chamber 311, the working volume of the entire compressor is V, and v=4v1=16es, that is, the displacement V of the compressor is 16eS in cubic millimeters.

As shown in fig. 16 and 21, the positions of the two exhaust ports 22 in the circumferential direction of the cylinder liner 20 coincide.

As shown in fig. 2, 9 and 17, 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 exhaust port 22 is disposed at an angle ranging from (arccos (2R/B) to 2 x arccos 2R/B) in the circumferential direction of the cylinder liner 20, where R is the inner radius of the cylinder liner 20 and B is the distance between two relatively parallel straight line segments of the projection of the slider 40 in the axial direction of the through hole 41. Thus, by reasonably optimizing the arrangement position of the exhaust port 22 in the circumferential direction of the cylinder liner 20, it is advantageous to avoid over-compression or under-compression of the compressor, and the angle range of θ in fig. 17 is (arccos (2R/B) to 2×arccos 2R/B), that is, the exhaust port 22 can be arranged in the above-described range in the circumferential direction of the cylinder liner 20.

As shown in fig. 10 to 18, the outer wall of the cylinder sleeve 20 is provided with an exhaust cavity 25, the exhaust port 22 is communicated to the exhaust cavity 25 by the inner wall of the cylinder sleeve 20, the fluid machine further comprises exhaust valve components, the exhaust valve components are arranged in the exhaust cavity 25 and correspond to the exhaust ports 22, the exhaust valve components are in two groups, and the two groups of exhaust valve components are respectively correspond to the two exhaust ports 22. In this way, the exhaust cavity 25 is used for accommodating the exhaust valve assembly, so that the occupied space of the exhaust valve assembly is effectively reduced, components are reasonably arranged, and the space utilization rate of the cylinder sleeve 20 is improved.

As shown in fig. 10 to 18, a communication hole 26 is further provided in the axial end surface of the cylinder liner 20, the communication hole 26 communicates with the exhaust chamber 25, 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. 16 and 21, the number of the exhaust chambers 25 is two, the two exhaust chambers 25 are arranged at intervals along the axial direction of the cylinder liner 20, and the two exhaust chambers 25 are arranged in one-to-one correspondence and communicate with the two exhaust ports 22. In this way, it is advantageous to reduce the throttling loss, thereby improving the performance of the compressor.

As shown in fig. 16, the two exhaust chambers 25 communicate through an exhaust communication hole 28, and the exhaust communication hole 28 extends in the axial direction of the cylinder liner 20. In this way, the communication reliability of the two exhaust chambers 25 is ensured.

Further, as shown in fig. 2, 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 connected to the cylinder liner 20 and sealing 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.

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

Optionally, the fastener is a screw.

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

As shown in fig. 18, the distance between the plane of the end of the exhaust port 22, which is in communication with the exhaust chamber 25, and the axis of the cylinder liner 20 is K, and the inner radius of the cylinder liner 20 is R, wherein 1mm +.k-R +.5 mm. Therefore, the value range of K-R is reasonably optimized, the reliability requirement of the compressor is met, on one hand, the problem that the cylinder sleeve wall at the exhaust port 22 is insufficient in strength due to the fact that the thickness of the cylinder sleeve wall at the exhaust port 22 is thinner due to the fact that K-R is too small is avoided, and the cylinder sleeve wall at the exhaust port 22 is easily broken due to high-frequency impact of a valve plate in a subsequent exhaust valve assembly; on the other hand, the excessive thickness of the cylinder liner wall at the exhaust port 22 caused by the excessive K-R is avoided, and the strength of the cylinder liner wall at the exhaust port 22 can meet the requirement, but the clearance volume is increased, so that the energy efficiency of the compressor is reduced and the amplitude is increased.

As shown in fig. 20 and 21, the cross-sectional area of the exhaust chamber 25 in the axial direction of the cylinder liner 20 is S2, the height of the single exhaust chamber 25 in the axial direction of the cylinder liner 20 is M, and the displacement of the fluid machine is V, wherein 0.5+.mxs2/v+.5. Thus, by reasonably optimizing the range of the ratio of the volume of the discharge chamber 25 to the displacement V of the compressor (fluid machine), it is ensured that the discharge chamber 25 can function to reduce the discharge noise and reduce the oil circulation rate at the time of high-speed operation of the compressor, where S2 is in square millimeters and M is in mm.

It should be noted that in this embodiment, as shown in fig. 22 and 23, another alternative embodiment may be provided, in which, an exhaust cavity 25 is formed on an outer wall of the cylinder liner 20, a boss structure 29 is disposed on a cavity wall surface of the exhaust cavity 25, and the exhaust port 22 is penetrated from an inner wall of the cylinder liner 20 to the boss structure 29 and is communicated with the exhaust cavity 25. Like this, boss structure 29 is the structural style of evagination, is favorable to reducing the discharge valve block of discharge valve subassembly and leads to opening the loss because of lubricating oil viscosity through setting up boss structure 29.

Further, as shown in fig. 23, the thickness of the boss structure 29 in the extending direction of the exhaust port 22 is N, where 0.05 mm+.n+.3 mm. Thus, on one hand, the wall thickness of the cylinder liner at the exhaust port 22 is increased, so that the strength of the cylinder liner wall at the position is ensured to be enough; on the other hand, the opening loss of the exhaust valve plate of the exhaust valve assembly can be reduced.

As shown in fig. 2, 10 to 19, the cylinder liner 20 has a radial suction hole 21 and a suction chamber 23, and the suction chamber 23 communicates with the radial suction hole 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. 2, 10 to 19, 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, the cylinder sleeve 20 is also provided with an air suction communication cavity 24, the two air suction cavities 23 are communicated with the air suction communication cavity 24, and the radial air suction holes 21 are communicated with the air suction cavities 23 through the air suction communication cavity 24. In this way, it is advantageous to increase the volume of the suction chamber 23, thereby reducing suction pressure pulsation.

Further, as shown in fig. 2, the suction communication chamber 24 extends a second predetermined distance in the axial direction of the cylinder liner 20, and at least one end of the suction communication chamber 24 penetrates through the axial end face of the cylinder liner 20. Thus, the air suction communication cavity 24 is conveniently formed on the end face of the cylinder sleeve 20, and the processing convenience of the air suction communication cavity 24 is ensured.

In the present embodiment, as shown in fig. 2, the upper flange 52 is provided with an exhaust passage 51, and the two exhaust ports 22 are communicated with the exhaust passage 51 through the exhaust chamber 25 and the communication hole 26.

Example two

It should be noted that the difference between the present embodiment and the first embodiment is that, as shown in fig. 25, the upper flange 52 and the lower flange 53 are both provided with the exhaust passage 51, and the exhaust port 22 on the upper side of the cylinder liner 20 is communicated with the exhaust passage 51 on the upper flange 52, and the exhaust port 22 on the lower side of the cylinder liner 20 is communicated with the exhaust passage 51 on the lower flange 53.

Example III

It should be noted that the difference between the present embodiment and the first embodiment is that, as shown in fig. 26, the cylinder liner 20 has two radial air intake holes 21, and the two radial air intake holes 21 are disposed at intervals along the axial direction of the cylinder liner 20, and the two radial air intake holes 21 are respectively communicated with the air intake chambers 23 on the corresponding sides.

Example IV

It should be noted that the difference between the present embodiment and the second embodiment is that, as shown in fig. 27, the cylinder liner 20 has two radial air intake holes 21, and the two radial air intake holes 21 are disposed at intervals along the axial direction of the cylinder liner 20, and the two radial air intake holes 21 are respectively communicated with the air intake chambers 23 on the corresponding sides.

Of course, in an embodiment of the present application, the upper flange 52 and the lower flange 53 may be used to suck air through the flanges 50, or one flange 50 of the two flanges 50 may be used to suck air together with the cylinder liner 20.

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

The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present application 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 the claims of the present application and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate such that embodiments of the application described herein may be implemented in sequences other than those illustrated or otherwise described herein.

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

Claims

1. A fluid machine, 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 cross groove structure (30) is rotatably arranged in the cylinder sleeve (20), 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) is provided with two 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 located in the sliding direction of the sliding block (40), and the crankshaft (10) rotates to drive the sliding block (40) to reciprocally slide in the limiting channels (31) and interact with the cross groove structure (30), so that the cross groove structure (30) and the sliding block (40) rotate in the cylinder sleeve (20);

the two flanges (50) are respectively arranged at two axial ends of the cylinder sleeve (20), and at least one flange (50) of the two flanges (50) is provided with an exhaust channel (51);

two exhaust ports (22) are formed in the side wall surface of the cylinder sleeve (20), the two exhaust ports (22) are arranged at intervals along the axial direction of the cylinder sleeve (20), and the two exhaust ports (22) are communicated with the exhaust channel (51);

the cross-sectional area of the hole cross section of the exhaust port (22) is S1, and the volume of the single variable volume cavity (311) is V1, wherein, the ratio of V1/S1 is more than or equal to 750 and less than or equal to 3300.

2. A fluid machine according to claim 1, wherein the positions of both exhaust ports (22) in the circumferential direction of the cylinder liner (20) coincide.

3. A fluid machine as claimed in claim 1, wherein,

the projection of the sliding block (40) in the axial direction of the through hole (41) is provided with two relatively parallel straight line sections and an arc line section connecting the end parts of the two straight line sections;

the exhaust port (22) is arranged in an angle range of (arccos (2R/B) to 2 x arccos (2R/B)) in the circumferential direction of the cylinder sleeve (20), wherein R is the inner circle radius of the cylinder sleeve (20), and B is the distance between two relatively parallel straight line segments of the projection of the sliding block (40) in the axial direction of the through hole (41).

4. The fluid machine according to claim 1, wherein the outer wall of the cylinder sleeve (20) is provided with an exhaust cavity (25), the exhaust port (22) is communicated to the exhaust cavity (25) by the inner wall of the cylinder sleeve (20), the fluid machine further comprises exhaust valve assemblies, the exhaust valve assemblies are arranged in the exhaust cavity (25) and correspond to the exhaust ports (22), the exhaust valve assemblies are two groups, and the two groups of exhaust valve assemblies are respectively correspond to the two exhaust ports (22).

5. The fluid machine according to claim 4, 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 communication hole (26) being in communication with the exhaust passage (51).

6. The fluid machine according to claim 4, wherein the number of the exhaust chambers (25) is two, the two exhaust chambers (25) are arranged at intervals along the axial direction of the cylinder sleeve (20), and the two exhaust chambers (25) are arranged and communicated with the two exhaust ports (22) in a one-to-one correspondence.

7. The fluid machine according to claim 6, wherein two of the exhaust chambers (25) are communicated through an exhaust communication hole (28), the exhaust communication hole (28) extending in an axial direction of the cylinder liner (20).

8. The fluid machine according to claim 4, wherein the distance between the plane of the end of the exhaust port (22) communicating with the exhaust chamber (25) and the axis of the cylinder liner (20) is K, and the inner radius of the cylinder liner (20) is R, wherein 1mm +.k-R +.5 mm.

9. The fluid machine according to claim 4, wherein the chamber cross-sectional area of the exhaust chamber (25) in the axial direction of the cylinder liner (20) is S2, the height of the exhaust chamber (25) in the axial direction of the cylinder liner (20) alone is M, and the displacement of the fluid machine is V, wherein 0.5+.ltoreq.m x S2)/v+.ltoreq.5.

10. The fluid machine according to claim 1, wherein an exhaust cavity (25) is formed in the outer wall of the cylinder sleeve (20), a boss structure (29) is arranged on the cavity wall surface of the exhaust cavity (25), and the exhaust port (22) penetrates through the boss structure (29) from the inner wall of the cylinder sleeve (20) and is communicated with the exhaust cavity (25).

11. The fluid machine according to claim 10, wherein the thickness of the boss structure (29) in the extension direction of the exhaust port (22) is N, wherein 0.05mm +.n+.3 mm.

12. The fluid machine according to claim 4 or 10, 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, which is connected to the cylinder liner (20) and seals the exhaust chamber (25).

13. The fluid machine according to any one of claims 1 to 11, 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.

14. A heat exchange device comprising a fluid machine, characterized in that the fluid machine is a fluid machine according to any one of claims 1 to 13.