EP4484750A1

EP4484750A1 - Fluid machine and heat exchange equipment

Info

Publication number: EP4484750A1
Application number: EP22943600.1A
Authority: EP
Inventors: Peilin Zhang; Zhongcheng DU; Zhi Li; Xuewei SONG; Ruibo YU; Liping Ren
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2022-05-23
Filing date: 2022-12-22
Publication date: 2025-01-01
Anticipated expiration: 2042-12-22
Also published as: CN117145768A; EP4484750A4; EP4484750B1; CN117145768B; WO2023226415A1

Abstract

A fluid machine and a heat exchange apparatus are provided. The fluid machine includes a crankshaft (10), a cylinder sleeve (20), a cross groove structure (30), a slide block (40) and two flanges (50), where the crankshaft (10) is provided with two eccentric portions (11); the crankshaft (10) and the cylinder sleeve (20) are arranged in an eccentric manner with a fixed eccentric distance; the cross groove structure (30) is rotatably disposed in the cylinder sleeve (20), two limiting channels (31) of the cross groove structure (30) are sequentially arranged in an axial direction, and the limiting channels (31) extend perpendicularly to an axial direction of the crankshaft (10); the two eccentric portions (11) correspondingly extend into two through holes (41) of the two slide blocks (40), at least one flange (50) has a first axial exhaust hole (511), and at least one flange (50) has a second axial exhaust hole (512); and an inclined notch (27) is provided at an edge of an inner circle of at least one end of the cylinder sleeve (20), the inclined notch (27) is in communication with the first axial exhaust hole (511), at least one exhaust port (22) is arranged on a side wall surface of the cylinder sleeve (20), and the exhaust port (22) is in communication with the second axial exhaust hole (512). The fluid machine has high energy efficiency, low noise and stable operation.

Description

Cross-Reference to Related Application

The present invention claims the priority to Chinese Patent Application No. 202210565477.9, filed on May 23, 2022 and entitled "Fluid machine and heat exchange apparatus", which is incorporated in its entirety herein by reference.

Technical Field

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

Background

A fluid machine in the related art includes a compressor, an expander, etc, and includes the compressor herein, for example.
The air-conditioning industry has been oriented towards high efficiency and low noise as per the national energy conservation and environment protection policy and the requirements of consumers for air-conditioning comfort. The compressor, the heart of an air conditioner, has a direct impact on the energy efficiency and noise level of the air conditioner. A rolling rotor compressor, the prevailing household air-conditioning compressor, has been fairly mature after nearly a century of development, with limited optimization space due to its structural principle.

Summary

A main objective of the invention is to provide a fluid machine and a heat exchange apparatus. According to an aspect of the present invention, a fluid machine is provided. The fluid machine includes a crankshaft, a cylinder sleeve, a cross groove structure, slide blocks, and two flanges. The crankshaft is provided with two eccentric portions in an axial direction of the crankshaft. The crankshaft and the cylinder sleeve are arranged in an eccentric manner with a fixed eccentric distance. The cross groove structure is rotatably arranged in the cylinder sleeve, the cross groove structure has two limiting channels, the two limiting channels are sequentially arranged in the axial direction of the crankshaft, and an extension direction of the limiting channels is perpendicular to the axial direction of the crankshaft. The slide blocks has through holes, two slide blocks are provided, the two eccentric portions correspondingly extend into the two through holes of the two slide blocks, the two slide blocks are correspondingly slidably arranged in the two limiting channels to form a volume-variable cavity, the volume-variable cavity is located in a slide direction of the slide blocks, and the crankshaft rotates to drive the slide blocks to interact with the cross groove structure while reciprocating in the limiting channels in a sliding manner, such that the cross groove structure and the slide blocks rotate in the cylinder sleeve. The two flanges are arranged at two axial ends of the cylinder sleeve respectively, at least one flange of the two flanges is provided with a first axial exhaust hole, and at least one flange of the two flanges is provided with a second axial exhaust hole. An inclined notch is provided at an edge of an inner circle of at least one of the two axial ends of the cylinder sleeve, the inclined notch is in communication with the first axial exhaust hole, at least one exhaust port is provided on a side wall surface of the cylinder sleeve, and the exhaust port is in communication with the second axial exhaust hole.
In some embodiments, the first axial exhaust hole and the second axial exhaust hole in the same flange are on a same radius of the flange, and the second axial exhaust hole is located on an outer peripheral side of the first axial exhaust hole.
In some embodiments, the flange at one end of the cylinder sleeve having the inclined notch is provided with the first axial exhaust hole, and the inclined notch is arranged opposite the first axial exhaust hole.
In some embodiments, a geometric center line of the first axial exhaust hole passes through a geometric center of the inclined notch.
In some embodiments, a projection of each slide block in a slide direction of the slide block is a part of a semicircle; and/or, an axial projection of each slide block in the through hole has two relatively parallel straight line segments and an arc segment connecting ends of the two straight line segments, and the exhaust port is arranged at a position in an angle range of (arccos (2R/B) - 2 * arccos (2R/B)) in a circumferential direction of the cylinder sleeve, where R is a radius of an inner circle of the cylinder sleeve, and B is a distance between the two relatively parallel straight line segments of the axial projection of the slide block in the through hole.
In some embodiments, an exhaust cavity is provided in an outer wall of the cylinder sleeve, the exhaust port is in communication with the exhaust cavity from an inner wall of the cylinder sleeve, the fluid machine further includes an exhaust valve assembly, and the exhaust valve assembly is arranged in the exhaust cavity and corresponds to the exhaust port. A communication hole is further provided in an axial end surface of the cylinder sleeve, the communication hole is in communication with the exhaust cavity, and the communication hole is in communication with the second axial exhaust hole.
In some embodiments, a distance between a plane where one end of the exhaust port in communication with the exhaust cavity and an axis of the cylinder sleeve is K, a radius of an inner circle of the cylinder sleeve is R, and 1 mm ≤ K - R ≤ 5 mm.
In some embodiments, a cavity sectional area of the exhaust cavity in an axial direction of the cylinder sleeve is S3, a height of the exhaust cavity in the axial direction of the cylinder sleeve is N, a displacement of the fluid machine is V, and 0.2 ≤ (N * S3)/V ≤ 5.
In some embodiments, an exhaust cavity is provided in an outer wall of the cylinder sleeve, a boss structure is arranged on a cavity wall surface of the exhaust cavity, and the exhaust port penetrates from an inner wall of the cylinder sleeve to the boss structure and is in communication with the exhaust cavity.
In some embodiments, a thickness of the boss structure in an extension direction of the exhaust port is M, and 0.05 mm ≤ M ≤ 3 mm.
In some embodiments, an area of a hole section of the exhaust port is S1, a volume of the single volume-variable cavity is V1, and 750 ≤ V1/S1 ≤ 3300.
In some embodiments, an inclined direction of the inclined notch extends from an end surface of one axial end of the cylinder sleeve to an axis of the cylinder sleeve, an included angle between the inclined notch and the end surface of the cylinder sleeve is α, and 15° ≤ α ≤ 60°.
In some embodiments, an equivalent diameter of a circle in which the inclined notch is located is D, a volume of the single volume-variable cavity is V1, and 400 ≤ V1/D ≤ 1000.
In some embodiments, a longitudinal section of the inclined notch through a diameter of the cylinder sleeve coincides with a longitudinal section of the exhaust port through the diameter of the cylinder sleeve.
In some embodiments, an area of a hole section of the first axial exhaust port is S4, a volume of the single volume-variable cavity is V1, and 750 ≤ V1/S4 ≤ 3300; and/or an area of a hole section of the second axial exhaust port is S2, a volume of the single volume-variable cavity is V1, and 50 ≤ V1/S2 ≤ 250.
In some embodiments, the exhaust cavity penetrates to an outer wall surface of the cylinder sleeve, the fluid machine further includes an exhaust cover plate, and the exhaust cover plate is connected to the cylinder sleeve and seals the exhaust cavity.
In some embodiments, a phase difference of a first included angle A exists between the two eccentric portions, eccentric amounts of the two eccentric portions are equal, a phase difference of a second included angle B exists between the extension directions of the two limiting channels, and the first angle A is twice of the second angle B.
In some embodiments, the first included angle A is 160°-200°, and the second included angle B is 80°-100°.
In some embodiments, each slide block has a pressing surface, facing an end of the limiting channel, and a projected area S_{slide block} of the pressing surface in the slide direction of the slide block and an area S_exhaust of the exhaust port of the cylinder sleeve satisfy that a value of S_{slide block}/S_exhaust is 8-25.
According to the other aspect of the present invention, a heat exchange apparatus is provided. The heat exchange apparatus includes a fluid machine. The fluid machine is the above fluid machine.

Brief Description of the Drawings

In order to more clearly illustrate technical solutions in the examples of the present application or in the traditional art, a brief introduction to the accompanying drawings required for the description of the examples or the prior art will be provided below. Apparently, the accompanying drawings in the following description are merely the examples of the present application, and those of ordinary skill in the art would also be able to derive other drawings from these disclosed drawings without making creative efforts.

Fig. 1 illustrates a schematic diagram of an internal structure of a compressor according to Example 1 of the present application;
Fig. 2 illustrates a schematic structural diagram of a pump assembly of the compressor in Fig. 1;
Fig. 3 illustrates an exploded view of the pump assembly in Fig. 2;
Fig. 4 illustrates a schematic structural diagram of assembling of a crankshaft, a cross groove structure and slide blocks in Fig. 3;
Fig. 5 illustrates a sectional schematic structural diagram of the crankshaft, the cross groove structure, and the slide blocks in Fig. 4;
Fig. 6 illustrates a schematic structural diagram of a shaft portion and eccentricity of two eccentric portions of the crankshaft in Fig. 4;
Fig. 7 illustrates a sectional schematic structural diagram of assembly eccentricity of a crankshaft and a cylinder sleeve in Fig. 3;
Fig. 8 illustrates a schematic structural diagram of eccentricity between a cylinder sleeve and a lower flange in Fig. 3;
Fig. 9 illustrates a schematic structural diagram of moving upwards of slide blocks in an axial direction of a through hole in Fig. 3;
Fig. 10 illustrates a schematic structural diagram of a state of the compressor in Fig. 3 at the beginning of suction;
Fig. 11 illustrates a schematic structural diagram of a state of the compressor in Fig. 3 in a suction process;
Fig. 12 illustrates a schematic structural diagram of a state of the compressor in Fig. 3 at the end of suction;
Fig. 13 illustrates a schematic structural diagram of a state of the compressor in Fig. 3 during air compression;
Fig. 14 illustrates a schematic structural diagram of a state of the compressor in Fig. 3 in an exhaust process;
Fig. 15 illustrates a schematic structural diagram of a state of the compressor in Fig. 3 at the end of exhaust;
Fig. 16 illustrates a schematic structural diagram of a cylinder sleeve in Fig. 3;
Fig. 17 illustrates a sectional schematic structural diagram of a cylinder sleeve in Fig. 3, in which an angle range of an exhaust port arranged in a circumferential direction of the cylinder sleeve is shown;
Fig. 18 illustrates a sectional schematic structural diagram of a cylinder sleeve in Fig. 3, in which a schematic diagram of a relation between K and R is shown;
Fig. 19 illustrates a sectional schematic structural diagram of a cylinder sleeve in Fig. 3, in which an angle range of an inclined notch arranged in a circumferential direction of the cylinder sleeve is shown;
Fig. 20 illustrates a sectional schematic structural diagram of a cylinder sleeve in Fig. 3 from another perspective, in which an included angle between an inclined notch and an end face of the cylinder sleeve is shown;
Fig. 21 illustrates a schematic structural diagram of an upper flange in Fig. 3 from a top view;
Fig. 22 illustrates a sectional schematic structural diagram of the pump assembly in Fig. 2 from another perspective, in which assembly eccentricity between a crankshaft and a cylinder sleeve is e;
Fig. 23 illustrates a schematic structural diagram of an exhaust cavity side of a cylinder sleeve in Fig. 3;
Fig. 24 illustrates a sectional schematic structural diagram of a cylinder sleeve in Fig. 2, in which a cross groove structure, slide blocks and a crankshaft are omitted;
Fig. 25 illustrates a schematic structural diagram of an exhaust cavity side of a cylinder sleeve according to an optional example of the present application, in which a boss structure is provided at an exhaust port;
Fig. 26 illustrates a partial sectional schematic structural diagram of the cylinder sleeve of Fig. 25;
Fig. 27 illustrates a schematic structural diagram of a cross section of a slide block in Fig. 3 in a slide direction of the slide block;
Fig. 28 illustrates a schematic structural diagram of a pump assembly according to Example 2 of the present application;
Fig. 29 illustrates a schematic structural diagram of a pump assembly according to Example 3 of the present application;
Fig. 30 illustrates a schematic structural diagram of a pump assembly according to Example 4 of the present application;
Fig. 31 illustrates a schematic structural diagram of a pump assembly according to Example 5 of the present application;
Fig. 32 illustrates a schematic structural diagram of a pump assembly according to Example 6 of the present application;
Fig. 33 illustrates a schematic structural diagram of a pump assembly according to Example 7 of the present application;
Fig. 34 illustrates a schematic structural diagram of a pump assembly according to Example 8 of the present application;
Fig. 35 illustrates a schematic diagram of a mechanism principle of operation of a compressor according to an optional example of the present application;
Fig. 36 illustrates a schematic diagram of the mechanism principle of operation of the compressor in Fig. 35;
Fig. 37 illustrates a schematic diagram of a mechanism principle of operation of a compressor in the related art;
Fig. 38 illustrates a schematic diagram of a mechanism principle of operation of a compressor improved in the related art;
Fig. 39 illustrates a schematic diagram of the mechanism principle of operation of the compressor in Fig. 38, in which a moment arm of a drive shaft driving a slide block to rotate is shown;
Fig. 40 illustrates a schematic diagram of the mechanism principle of operation the compressor in Fig. 38, in which a center of a limiting groove structure coincides with a center of an eccentric portion; and
Fig. 41 illustrates a schematic diagram of change curves of an exhaust loss, a coefficient of performance (COP) and a clearance volume of a compressor with V1/S1.

The drawings include the following reference numerals:
10. crankshaft; 11. eccentric portion; 12. shaft portion; 20. cylinder sleeve; 21. radial suction hole; 22. exhaust port; 23. suction cavity; 24. suction communication cavity; 25. exhaust cavity; 26. communication hole; 27. inclined notch; 29. boss structure; 30. cross groove structure; 31. limiting channel; 311. volume-variable cavity; 32. central hole; 40. slide block; 41. through hole; 42. pressing surface; 50, flange; 511. first axial exhaust hole; 512. second axial exhaust hole; 52. upper flange; 53. lower flange; 70. exhaust cover plate; 80. liquid separator component; 81. housing assembly; 82. motor assembly; 83. pump assembly; 84. upper cover assembly; and 85. lower cover assembly.

Detailed Description of the Embodiments

The technical solutions in examples of the invention are clearly and completely described below with reference to the accompanying drawings in the examples of the invention. Apparently, the examples described are merely some examples rather than all examples of the invention. Based on the examples of the invention, all other examples derived by those of ordinary skill in the art without making creative efforts fall within the scope of protection of the invention.
In the art known to inventors, as shown in Fig. 37, a mechanism principle of operation of a compressor is proposed based on a cross slide block mechanism, that is, a cylinder is eccentrically arranged with respect to a drive shaft with a point O₁ as a cylinder center, a point O₂ as a drive shaft center, and a point O₃ as a slide block center. The slide block center O₃ moves circularly on a circle having a diameter of O₁O₂.
In the above mechanism principle of operation, the cylinder center O₁ and the drive shaft center O₂ serve as two rotation centers of a motion mechanism. Moreover, a midpoint O₀ of a line segment O₁O₂ serves as a virtual center of the slide block center O₃, such that the slide block reciprocates relative to the cylinder and also reciprocates relative to the drive shaft.
Since the midpoint O₀ of the line segment O₁O₂ is a virtual center, no balance system can be set, resulting in a problem that high frequency vibration characteristics of the compressor are deteriorated. Based on the above mechanism principle of operation, as shown in Fig. 38, a motion mechanism with O₀ as the drive shaft center is provided, that is, the cylinder center O₁ and the drive shaft center O₀ serve as two rotation centers of the motion mechanism. The drive shaft has an eccentric portion, the slide block is arranged coaxial with the eccentric portion, and assembly eccentricity of the drive shaft and the cylinder is equal to eccentricity of the eccentric portion, such that the slide block center O₃ moves circularly around the drive shaft center O₀ with O₁O₀ as a radius.
Correspondingly, an operating mechanism is proposed. The operating mechanism includes a cylinder, a limiting groove structure, a slide block and a drive shaft. The limiting groove structure is rotatably arranged in the cylinder. The cylinder and the limiting groove structure are coaxially arranged, that is, the cylinder center O₁ is also a center of the limiting groove structure. The slide block reciprocates relative to the limiting groove structure. The slide block is assembled coaxial with the eccentric portion of the drive shaft. The slide block moves circularly around a shaft portion of the drive shaft. A specific motion process is as follows: the drive shaft rotates to drive the slide block to revolve around a center of the shaft portion of the drive shaft, the slide block rotates relative to the eccentric portion at the same time, and the slide block reciprocates in a limiting groove of the limiting groove structure and pushes the limiting groove structure to rotate.
However, as shown in Fig. 39, a length of a moment arm L of the drive shaft driving the slide block to rotate is L = 2e * cosθ * cosθ, where e is eccentricity of the eccentric portion, and θ is an included angle between the connecting line O₁O₀ and a slide direction of the slide block in the limiting groove.
As shown in Fig. 40, when the cylinder center O₁ (that is, a center of the limiting groove structure) coincides with a center of the eccentric portion, a resultant force of a drive force of the drive shaft passes through the center of the limiting groove structure, that is, torque applied to the limiting groove structure is zero. The limiting groove structure cannot rotate. In this case, the motion mechanism is at a dead point position, and the slide block cannot be driven to rotate.
Based on this, the present application provides a brand-new mechanism principle of a cross groove structure with two limiting channels and double slide blocks, and constructs a brand-new compressor based on the principle. The compressor has the characteristics of high energy efficiency and low noise. The compressor is taken as an example to specifically introduce a fluid machine based on the cross groove structure with two limiting channels and double slide blocks.
In order to solve the problems of low energy efficiency and high noise of a compressor in the related art, the present application provides a fluid machine, a heat exchange apparatus, and an operation method of the fluid machine. The heat exchange apparatus includes the following fluid machine. The fluid machine is operated through the following operation method.
The fluid machine in the examples of the present application includes a crankshaft 10, a cylinder sleeve 20, a cross groove structure 30, and slide blocks 40. The crankshaft 10 is provided with two eccentric portions 11 in an axial direction of the crankshaft. A phase difference of a first included angle A is provided between the two eccentric portions 11, and eccentricity of the two eccentric portions 11 is equal. The crankshaft 10 and the cylinder sleeve 20 are arranged in an eccentric manner with a fixed eccentric distance. The cross groove structure 30 is rotatably arranged in the cylinder sleeve 20. The cross groove structure 30 has two limiting channels 31. The two limiting channels 31 are sequentially arranged in the axial direction of the crankshaft 10. An extension direction of the limiting channels 31 is perpendicular to the axial direction of the crankshaft 10. A phase difference of a second included angle B is provided between extension directions of the two limiting channels 31. The first included angle A is twice of the second included angle B. The slide blocks 40 has through holes 41. Two slide blocks 40 are provided. The two eccentric portions 11 correspondingly extend into the two through holes 41 of the two slide blocks 40. The two slide blocks 40 are correspondingly slidably arranged in the two limiting channels 31 to form a volume-variable cavity 311. The volume-variable cavity 311 is located in a slide direction of the slide blocks 40. The crankshaft 10 rotates to drive the slide blocks 40 to interact with the cross groove structure 30 while reciprocating in the limiting channels 31 in a sliding manner, such that the cross groove structure 30 and the slide blocks 40 rotate in the cylinder sleeve 20.
By configuring a structure form that the cross groove structure 30 has two limiting channels 31 and correspondingly providing two slide blocks 40, the two eccentric portions 11 of the crankshaft correspondingly extend into the two through holes 41 of the two slide blocks 40. Moreover, the two slide blocks 40 are slidably arranged in the two limiting channels 31 correspondingly to form the volume-variable cavity 311. Since the first included angle A between the two eccentric portions 11 is twice of the second included angle B between the extension directions of the two limiting channels 31, when one of the two slide blocks 40 is at the dead center position, that is, drive torque of the eccentric portion 11 corresponding to the slide block 40 at the dead center position is 0, the slide block 40 at the dead center position cannot continue to rotate, at this time, driving torque of the other eccentric portion 11 of the two eccentric portion 11 driving the corresponding slide block 40 has a maximum value, and it is guaranteed that the eccentric portion 11 having the maximum driving torque can normally drive the corresponding slide block 40 to rotate, such that the slide block 40 drives the cross groove structure 30 to rotate, and further drives the slide block 40 at the dead point position to continue rotating by means of the cross groove structure 30. Stable operation of the fluid machine is achieved, the dead point position of the motion mechanism is avoided, motion reliability of the fluid machine is improved, and operation reliability of the heat exchange apparatus is guaranteed.
Moreover, since the fluid machine provided in the examples of the present application can operate stably, that is, the compressor is guaranteed to have higher energy efficiency and lower noise, operation reliability of the heat exchange apparatus is guaranteed.
In the examples of the present application, neither the first included angle A nor the second included angle B is zero.
As shown in Figs. 35 and 36, during operation of the fluid machine, the crankshaft 10 rotates around an axis O₀ of the crankshaft 10. The cross groove structure 30 revolves around the axis O₀ of the crankshaft 10, and the axis O₀ of the crankshaft 10 and an axis O₁ of the cross groove structure 30 are arranged in an eccentric manner with a fixed distance. The first slide block 40 moves circularly around the axis O₀ of the crankshaft 10, a distance between a center O₃ of the first slide block 40 and the axis O₀ of the crankshaft 10 is equal to eccentricity of the first eccentric portion 11 corresponding to the crankshaft 10, and the eccentricity is equal to an eccentric distance between the axis O₀ of the crankshaft 10 and the axis O1 of the cross groove structure 30. The crankshaft 10 rotates to drive the first slide block 40 to move circularly, and the first slide block 40 interacts with the cross groove structure 30 and reciprocates in the limiting channel 31 of the cross groove structure 30 in a sliding manner. The second slide block 40 moves circularly around the axis O₀ of the crankshaft 10, a distance between a center O₄ of the second slide block 40 and the axis O₀ of the crankshaft 10 is equal to eccentricity of the second eccentric portion 11 corresponding to the crankshaft 10, and the eccentricity is equal to an eccentric distance between the axis O₀ of the crankshaft 10 and the axis O₁ of the cross groove structure 30. The crankshaft 10 rotates to drive the second slide block 40 to move circularly, and the second slide block 40 interacts with the cross groove structure 30 and reciprocates in the limiting channel 31 of the cross groove structure 30 in a sliding manner.
The fluid machine operating according to the above method forms a cross slide block mechanism. The operation method adopts a cross slide block mechanism principle. The two eccentric portions 11 of the crankshaft 10 serve as a first connecting rod L₁ and a second connecting rod L₂ respectively. The two limiting channels 31 of the cross groove structure 30 serve as a third connecting rod L₃ and a fourth connecting rod L₄ respectively. Lengths of the first connecting rod L₁ and the second connecting rod L₂ are equal (please refer to Fig. 35).
As shown in Fig. 35, a first included angle A is formed between the first connecting rod L₁ and the second connecting rod L₂. A second included angle B is formed between the third connecting rod L₃ and the fourth connecting rod L₄. The first included angle A is twice of the second included angle B.
As shown in Fig. 36, a connecting line between the axis O₀ of the crankshaft 10 and the axis O₁ of the cross groove structure 30 is a connecting line O₀O₁. A third included angle C is formed between the first connecting rod L₁ and the connecting line O₀O₁. Correspondingly, a fourth included angle D is formed between the third connecting rod L₃ and the connecting line O₀O₁. The third included angle C is twice of the fourth included angle D. A fifth included angle E is formed between the second connecting rod L₂ and the connecting line O₀O₁. Correspondingly, a sixth included angle F is formed between the fourth connecting rod L₄ and the connecting line O₀O₁. The fifth included angle E is twice of the sixth included angle F. A sum of the third included angle C and the fifth included angle E is the first included angle A, and a sum of the fourth included angle D and the sixth included angle F is the second included angle B.
Further, the operation method further includes that a rotation angular velocity of the slide blocks 40 relative to the eccentric portions 11 is the same as a revolution angular velocity of the slide blocks 40 around the axis O₀ of the crankshaft 10, and a revolution angular velocity of the cross groove structure 30 around the axis O₀ of the crankshaft 10 is the same as the rotation angular velocity of the slide blocks 40 relative to the eccentric portions 11.
In some embodiments, the axis O₀ of the crankshaft 10 corresponds to a rotation center of the first connecting rod L₁ and the second connecting rod L₂, and the axis O₁ of the cross groove structure 30 corresponds to a rotation center of the third connecting rod L₃ and the fourth connecting rod L₄. The two eccentric portions 11 of the crankshaft 10 serve as the first connecting rod L₁ and the second connecting rod L₂ respectively, and the two limiting channels 31 of the cross groove structure 30 serve as the third connecting rod L₃ and the fourth connecting rod L₄ respectively. The lengths of the first connecting rod L₁ and the second connecting rod L₂ are equal. In this way, when the crankshaft 10 rotates, the eccentric portions 11 on the crankshaft 10 drive the corresponding slide blocks 40 to revolve around the axis O₀ of the crankshaft 10, and meanwhile, the slide blocks 40 can rotate relative to the eccentric portions 11 and have a same relative rotation speed. Since the first slide block 40 and the second slide block 40 reciprocate in the two corresponding limiting channels 31 respectively and drive the cross groove structure 30 to move circularly, the motion directions of the two slide blocks 40 always have a phase difference of the second included angle B due to limitation of the two limiting channels 31 of the cross groove structure 30. When one of the two slide blocks 40 is at the dead center position, the eccentric portion 11 for driving the other slide block 40 has the largest driving torque, and the eccentric portion 11 with the largest driving torque can normally drive the corresponding slide block 40 to rotate, such that the slide block 40 drives the cross groove structure 30 to rotate, and further drives the slide block 40 at the dead point position to continue rotating through the cross groove structure 30. Therefore, stable operation of the fluid machine is achieved, the dead point position of the motion mechanism is avoided, motion reliability of the fluid machine is improved, and operation reliability of the heat exchange apparatus is guaranteed.
In the present application, a maximum moment arm of the driving torque of the eccentric portion 11 is 2e.
In such a motion method, a motion track of the slide block 40 is a circle, and the circle has the axis O₀ of the crankshaft 10 as a center and the line O₀O₁ as a radius.
In the present application, during rotation of the crankshaft 10, the crankshaft 10 rotates twice to complete four suction and exhaust processes.
In order to solve the problems of low energy efficiency and high noise of a compressor in the related art, the present application provides a fluid machine, and a heat exchange apparatus. The heat exchange apparatus includes a fluid machine. The fluid machine is the fluid machine described above and described below.

Example 1

As shown in Figs. 1-27, a fluid machine further includes a flange 50. The flange 50 is arranged at an axial end of a cylinder sleeve 20. A crankshaft 10 and the flange 50 are concentrically arranged. A cross groove structure 30 and the cylinder sleeve 20 are coaxially arranged. Assembly eccentricity of the crankshaft 10 and the cross groove structure 30 is determined by a relative positional relation between the flange 50 and the cylinder sleeve 20. The flange 50 is fixed on the cylinder sleeve 20 by means of a fastener. Relative positions of an axis of the flange 50 and an axis of an inner ring of the cylinder sleeve 20 is controlled by centering of the flange 50. The relative positions of the axis of the flange 50 and the axis of the inner ring of the cylinder sleeve 20 determines relative positions of an axis of the crankshaft 10 and an axis of the cross groove structure 30. The essence of centering of the flange 50 is to make eccentricity of an eccentric portion 11 equal to assembly eccentricity of the crankshaft 10 and the cylinder sleeve 20.
In some embodiments, as shown in Fig. 6, the eccentricity of the two eccentric portions 11 are equal to e. As shown in Fig. 7, assembly eccentricity between the crankshaft 10 and the cylinder sleeve 20 is e (since the cross groove structure 30 and the cylinder sleeve 20 are coaxially arranged, the assembly eccentricity between the crankshaft 10 and the cross groove structure 30 is the assembly eccentricity between the crankshaft 10 and the cylinder sleeve 20). The flange 50 includes an upper flange 52 and a lower flange 53. As shown in Fig. 8, a distance between an inner ring axis of the cylinder sleeve 20 and an inner ring axis of the lower flange 53 is e, that is, equal to the eccentricity of the eccentric portions 11.
In some embodiments, a first assembly clearance is provided between the crankshaft 10 and the flange 50, and the first assembly clearance has a range of 0.005 mm-0.05 mm.
In some embodiments, the first assembly clearance has a range of 0.01 mm-0.03 mm.
In some embodiments, two slide blocks 40 are arranged concentric with the two eccentric portions 11 respectively. The slide blocks 40 move circularly around the axis of the crankshaft 10. A first rotation gap is provided between a wall of a through hole 41 and the eccentric portions 11. The first rotation gap has a range of 0.005 mm-0.05 mm.
In some embodiments, a second rotation gap is provided between an outer peripheral surface of the cross groove structure 30 and an inner wall surface of the cylinder sleeve 20. The second rotation gap has a size of 0.005 mm-0.1 mm.
As shown in Figs. 2-7, a shaft portion 12 of the crankshaft 10 is integrally formed, and the shaft portion 12 has only one axis. In this way, one-step forming of the shaft portion 12 is facilitated, so as to reduce difficulty in manufacturing the shaft portion 12.
In an example of the present application which is not shown, the shaft portion 12 of the crankshaft 10 includes a first section and a second section connected in an axial direction of the shaft portion. The first section and the second section are coaxially arranged. The two eccentric portions 11 are arranged on the first section and the second section respectively.
In some embodiments, the first section is detachably connected to the second section. In this way, ease of assembly and disassembly of the crankshaft 10 is guaranteed.
As shown in Figs. 2-7, the shaft portion 12 of the crankshaft 10 and the eccentric portions 11 are integrally formed. Thus, one-step forming of the crankshaft 10 is facilitated, so as to reduce difficulty in manufacturing the crankshaft 10.
In an example of the present application which is not shown, the shaft portion 12 of the crankshaft 10 is detachably connected to the eccentric portions 11. In this way, installation and disassembly of the eccentric portions 11 are facilitated.
As shown in Figs. 3 and 4, two ends of the limiting channel 31 penetrate to an outer peripheral surface of the cross groove structure 30. Thus, difficulty in manufacturing the cross groove structure 30 can be reduced.
In the present application, the first included angle A is 160°-200°, and the second included angle B is 80°-100°, as long as a relation that the first included angle A is twice of the second included angle B.
In some embodiments, the first included angle A is 160°, and the second included angle B is 80°.
In some embodiments, the first included angle A is 165°, and the second included angle B is 82.5°.
In some embodiments, the first included angle A is 170°, and the second included angle B is 85°.
In some embodiments, the first included angle A is 175°, and the second included angle B is 87.5°.
In some embodiments, the first included angle A is 180°, and the second included angle B is 90°.
In some embodiments, the first included angle A is 185°, and the second included angle B is 92.5°.
In some embodiments, the first included angle A is 190°, and the second included angle B is 95°.
In some embodiments, the first included angle A is 195°, and the second included angle B is 97.5°.
In the present application, each eccentric portion 11 has a circular arc surface. A central angle of the circular arc surface is 180° or above. In this way, it is guaranteed that the circular arc surfaces of the eccentric portions 11 can apply an effective drive force to the slide blocks 40, such that reliability of movement of the slide blocks 40 can be guaranteed.
As shown in Figs. 2-7, each eccentric portion 11 has a cylindrical shape.
In some embodiments, a proximal end of the eccentric portion 11 is flush with an outer circle of the shaft portion 12 of the crankshaft 10.
In some embodiments, the proximal end of the eccentric portion 11 protrudes beyond the outer circle of the shaft portion 12 of the crankshaft 10.
In some embodiments, the proximal end of the eccentric portion 11 is located on an inner side of the outer circle of the shaft portion 12 of the crankshaft 10.
In an example of the present application which is not shown, the slide blocks 40 include a plurality of sub-structures, and the plurality of sub-structures are spliced to define through holes 41.
As shown in Figs. 2-7, the two eccentric portions 11 are spaced in the axial direction of the crankshaft 10. In this way, in a process of assembling the crankshaft 10, the cylinder sleeve 20 and the two slide blocks 40, it is guaranteed that a separation distance between the two eccentric portions 11 can provide an assembly space for the cylinder sleeve 20, so as to guarantee convenience of assembly.
As shown in Fig. 3, the cross groove structure 30 has a central hole 32. The two limiting channels 31 are in communication through the central hole 32. A diameter of the central hole 32 is greater than that of the shaft portion 12 of the crankshaft 10. In this way, it is guaranteed that the crankshaft 10 can smoothly pass through the central hole 32.
In some embodiments, the diameter of the central hole 32 is greater than that of the eccentric portions 11. In this way, it is guaranteed that the eccentric portions 11 of the crankshaft 10 can smoothly pass through the central hole 32.
As shown in Fig. 9, an axial projection of each slide block 40 in the through hole 41 has two relatively parallel straight line segments and an arc segment connecting ends of the two straight line segments. The limiting channels 31 have a set of first slide surfaces arranged oppositely and making slide contact with the slide blocks 40. The slide blocks 40 have second slide surfaces matching the first slide surfaces. The slide blocks 40 have pressing surfaces 42 facing ends of the limiting channels 31. The pressing surfaces 42 serve as heads of the slide blocks 40. The two second slide surfaces are connected by the pressing surfaces 42. The pressing surfaces 42 face a volume-variable cavity 311. Thus, a projection of the second slide surface of each slide block 40 in an axial direction of the through hole 41 is a straight line segment, and a projection of the pressing surface 42 of the slide block 40 in the axial direction of the through hole 41 is an arc segment.
Specifically, the pressing surfaces 42 are arc surfaces. A distance between arc centers of the arc surfaces and centers of the through holes 41 is equal to the eccentricity of the eccentric portions 11. In Fig. 9, the center of the through holes 41 of the slide blocks 40 is O_{slide block}, the distance between the arc center of each of the two arc surfaces and the center of the through holes 41 is e, that is, the eccentricity of the eccentric portions 11. Dotted lines X in Fig. 9 indicate circles in which the arc centers of the two arc surfaces are located.
In some embodiments, a radius of curvature of the arc surfaces is equal to a radius of the inner circle of the cylinder sleeve 20.
In some embodiments, the radius of curvature of the arc surfaces has a difference value from the radius of the inner circle of the cylinder sleeve 20 in a range of -0.05 mm-0.025 mm.
In some embodiments, the difference value has a range of -0.02 mm-0.02 mm.
In the present application, a projected area S_{slide block} of each pressing surface 42 in the slide direction of the slide block 40 and an area S_exhaust of a compression exhaust port 22 of the cylinder sleeve 20 satisfy a condition that a value of S_{slide block}/S_exhaust is 8-25.
In some embodiments, the value of S_{slide block}/S_exhaust is 12-18.
The fluid machine shown in the example is a compressor. As shown in Fig. 1, the compressor includes a liquid separator component 80, a housing assembly 81, a motor assembly 82, a pump assembly 83, an upper cover assembly 84 and a lower cover assembly 85. The liquid separator component 80 is arranged outside the housing assembly 81. The upper cover assembly 84 is assembled at an upper end of the housing assembly 81. The lower cover assembly 85 is assembled at a lower end of the housing assembly 81. Both the motor assembly 82 and the pump assembly 83 are located inside the housing assembly 81. The motor assembly 82 is located above the pump assembly 83, and alternatively, the motor assembly 82 is located below the pump assembly 83. The pump assembly 83 of the compressor includes the crankshaft 10, the cylinder sleeve 20, the cross groove structure 30, the slide blocks 40, the upper flange 52 and the lower flange 53 described above.
In some embodiments, the components are connected by welding, shrink fitting, or cold pressing.
An assembly process of the entire pump assembly 83 is as follows: the lower flange 53 is fixed on the cylinder sleeve 20, the two slide blocks 40 are arranged in the corresponding two limiting channels 31 respectively, the two eccentric portions 11 of the crankshaft 10 extend into the two through holes 41 of the corresponding two slide blocks 40 respectively, then the crankshaft 10, the cross groove structure 30 and the two slide blocks 40 that are assembled are arranged in the cylinder sleeve 20, one end of the crankshaft 10 is installed on the lower flange 53, and the other end of the crankshaft 10 penetrates the upper flange 52, as shown in Figs. 2 and 3 for details.
In the example, enclosed spaces defined by the slide blocks 40, the limiting channels 31, the cylinder sleeve 20 and the upper flange 52(or the lower flange 53) are the variable volume cavities 311. The pump assembly 83 has four variable volume cavities 311 in total. During rotation of the crankshaft 10, the crankshaft 10 rotates twice, and a single volume-variable cavity 311 completes one suction and exhaust process. For the compressor, the crankshaft 10 rotates twice, and four suction and exhaust processes are completed in total.
Further, the enclosed spaces defined by the pressing surfaces 42 of the heads of the slide blocks 40, two side wall surfaces and bottom surfaces of the limiting channels 31, a part of an inner wall surface of the cylinder sleeve 20, and a part of a surface of the upper flange 52 facing the cylinder sleeve 20 (or a part of a surface of the lower flange 53 facing the cylinder sleeve 20) is the variable volume cavities 311.
As shown in Figs. 10-15, the slide blocks 40 rotate relative to the cylinder sleeve 20 while reciprocating in the limiting channels 31. In Figs. 10-12, the variable volume cavities 311 increase when the slide blocks 40 rotate clockwise from 0° to 180°. In a process of increasing of the variable volume cavities 311, the variable volume cavities 311 are in communication with a suction cavity 23 of the cylinder sleeve 20. When the slide blocks 40 rotate to 180°, a volume of the variable volume cavities 311 reaches a maximum value. At this time, the variable volume cavities 311 are separated from the suction cavity 23, such that suction operation is completed. In Figs. 13-15, the slide blocks 40 continue to rotate clockwise from 180° to 360°, and the variable volume cavities 311 are reduced. The slide blocks 40 compress air in the variable volume cavities 311. When the slide blocks 40 rotate until the variable volume cavities 311 are in communication with the compression exhaust port 22, and the air in the variable volume cavities 311 reaches exhaust pressure, an exhaust valve plate 61 of an exhaust valve assembly 60 is opened to start exhaust operation. After compression is completed, a next cycle is started.
As shown in Figs. 10-15, a point marked with M is taken as a reference point of relative motion of the slide blocks 40 and the crankshaft 10. Fig. 11 shows a process of clockwise rotation of the slide blocks 40 from 0° to 180°, an angle of rotation of the slide blocks 40 is θ1, and a corresponding angle of rotation of the crankshaft 10 is 2θ1. Fig. 13 shows a process of continuous clockwise rotation of the slide blocks 40 from 180° to 360°, an angle of rotation of the slide blocks 40 is 180° + θ2, and a corresponding angle of rotation of the crankshaft 10 is 360° + 2θ2. Fig. 14 shows a process of continuous clockwise rotation of the slide blocks 40 from 180° to 360°, the variable volume cavities 311 are in communication with the compression exhaust port 22, an angle of rotation of the slide blocks 40 is 180° + θ3, and a corresponding angle of rotation of the crankshaft 10 is 360° + 2θ3, that is, one rotation of the slide blocks 40 corresponds to two rotations of the crankshaft 10, where θ1 < θ2 < θ3.
Operation of the compressor is described in detail below.
As shown in Fig. 1, the motor assembly 82 drives the crankshaft 10 to rotate. The two eccentric portions 11 of the crankshaft 10 drive the corresponding two slide blocks 40 to move respectively. While the slide blocks 40 revolve around the axis of the crankshaft 10, the slide blocks 40 rotate relative to the eccentric portions 11. The slide blocks 40 reciprocate along the limiting channels 31, and drive the cross groove structure 30 to rotate in the cylinder sleeve 20. The slide blocks 40 reciprocate along the limiting channels 31 while revolving, thereby constituting a motion mode of the cross slide block mechanism.
For the problem of how to reduce an exhaust loss, the present application combines exhaust at an end surface of the flange 50 and exhaust at a side of the cylinder sleeve 20 to reduce the exhaust loss of the compressor, specifically as follows:
As shown in Figs. 1-27, at least one flange 50 of the two flanges 50 is provided with a first axial exhaust hole 511, and at least one flange 50 of the two flanges 50 is provided with a second axial exhaust hole 512. An inclined notch 27 is provided at an edge of an inner circle of at least one of the two axial ends of the cylinder sleeve 20. The inclined notch 27 is in communication with the first axial exhaust hole 511. At least one exhaust port 22 is provided on a side wall surface of the cylinder sleeve 20. The exhaust port 22 is in communication with the second axial exhaust hole 512.
At least one flange 50 of the two flanges 50 is provided with the first axial exhaust hole 511, and at least one flange 50 of the two flanges 50 is provided with the second axial exhaust hole 512. Moreover, the inclined notch 27 is provided at the edge of the inner circle of at least one of the two axial ends of the cylinder sleeve 20. The inclined notch 27 is in communication with the first axial exhaust hole 511. At least one exhaust port 22 is provided on the side wall surface of the cylinder sleeve 20. The exhaust port 22 is in communication with the second axial exhaust hole 512. In this way, exhaust reliability of the fluid machine is guaranteed, such that the exhaust loss of the fluid machine is reduced, and efficiency of the fluid machine is improved.
As shown in Figs. 2 and 21, the first axial exhaust hole 511 and the second axial exhaust hole 512 in the same flange 50 are on a same radius of the flange 50. The second axial exhaust hole 512 is located on an outer peripheral side of the first axial exhaust hole 511. In this way, throttle loss is reduced advantageously, thereby improving performance of the compressor. Moreover, design difficulty and manufacturing difficulty of the flanges 50 are reduced. It is easy to find out a reason and analyze it when an abnormal situation occurs later.
As shown in Figs. 2 and 16, the flange 50 at one end of the cylinder sleeve 20 having the inclined notch 27 is provided with the first axial exhaust hole 511, and the inclined notch 27 is arranged opposite the first axial exhaust hole 511. Thus, exhaust reliability of the variable volume cavities 311 in communication with the inclined notch 27 is guaranteed.
Further, a geometric center line of the first axial exhaust hole 511 passes through a geometric center of the inclined notch 27. In this way, exhaust loss is reduced advantageously, thereby guaranteeing that the efficiency of the compressor can be optimized.
In some embodiments, a projection of each slide block 40 in a slide direction of the slide block is a part of a semicircle.
As shown in Figs. 2, 9 and 17, an axial projection of each slide block 40 in the through hole 41 has two relatively parallel straight line segments and an arc segment connecting ends of the two straight line segments. The exhaust port 22 is arranged at a position in an angle range of (arccos (2R/B) - 2 * arccos 2R/B) in a circumferential direction of the cylinder sleeve 20. R is a radius of an inner circle of the cylinder sleeve 20, and B is a distance between the two relatively parallel straight line segments of the axial projection of the slide block 40 in the through hole 41. In this way, by reasonably optimizing the position of the exhaust port 22 arranged in the circumferential direction of the cylinder sleeve 20, overcompression or undercompression of the compressor can be avoided. The angle range of θ in Fig. 17 is (arccos (2R/B) - 2 * arccos 2R/B), that is, the exhaust port 22 can be arranged within the above range in the circumferential direction of the cylinder sleeve 20.
As shown in Figs. 10-18, an exhaust cavity 25 is provided in an outer wall of the cylinder sleeve 20. The exhaust port 22 is in communication with the exhaust cavity 25 from an inner wall of the cylinder sleeve 20. The fluid machine further includes an exhaust valve assembly, and the exhaust valve assembly is arranged in the exhaust cavity 25 and corresponds to the exhaust port 22. In this way, the exhaust cavity 25 is configured to accommodate the exhaust valve assembly, so as to effectively reduce an occupied space of the exhaust valve assembly, such that the components are reasonably arranged, and a space utilization rate of the cylinder sleeve 20 is improved.
As shown in Figs. 10-18, a communication hole 26 is further provided in an axial end surface of the cylinder sleeve 20. The communication hole 26 is in communication with the exhaust cavity 25. The communication hole 26 is in communication with the second axial exhaust hole 512. In this way, exhaust reliability of the cylinder sleeve 20 is guaranteed.
Further, as shown in Fig. 2, the exhaust cavity 25 penetrates to an outer wall surface of the cylinder sleeve 20. The fluid machine further includes an exhaust cover plate 70. The exhaust cover plate 70 is connected to the cylinder sleeve 20 and seals the exhaust cavity 25. Thus, the exhaust cover plate 70 isolates the variable volume cavities 311 from an outer space of the pump assembly 83.
In some embodiments, the exhaust cover plate 70 is fixed on the cylinder sleeve 20 by means of a fastener.
In some embodiments, the fastener is a screw.
In some embodiments, an outer contour of exhaust cover plate 70 is adapted to an outer contour of exhaust cavity 25.
As shown in Fig. 18, a distance between a plane where one end of the exhaust port 22 in communication with the exhaust cavity 25 and an axis of the cylinder sleeve 20 is K, a radius of an inner circle of the cylinder sleeve 20 is R, and 1 mm ≤ K - R ≤ 5 mm. In this way, by reasonably optimizing a value range of K - R, reliability requirements on the compressor are satisfied. On one hand, a situation that a cylinder sleeve wall at the exhaust port 22 is too thin due to too small K - R, resulting in insufficient strength of the cylinder sleeve wall at the exhaust port 22, and the cylinder sleeve wall at the exhaust port 22 is likely to be broken due to subsequent high-frequency impact of the valve plate in the exhaust valve assembly is avoided. On the other hand, a situation that the cylinder sleeve wall at the exhaust port 22 is too thick due to excessive K - R, although the strength of the cylinder sleeve wall at the exhaust port 22 can satisfy the requirements, and the clearance volume is increased, resulting in an increase in energy efficiency reduction of the compressor is avoided.
As shown in Figs. 23 and 24, a cavity sectional area of the exhaust cavity 25 in an axial direction of the cylinder sleeve 20 is S3, a height of the exhaust cavity 25 in the axial direction of the cylinder sleeve 20 is N, a displacement of the fluid machine is V, and 0.2 ≤ (N * S3)/V ≤ 5. In this way, it is guaranteed that the exhaust cavity 25 can reduce exhaust noise and an oil circulation rate during high-speed operation of the compressor by reasonably optimizing a range of a ratio of the volume of the exhaust cavity 25 to the displacement V of the compressor (fluid machine). S3 is in square millimeters, and N is in mm.
In the example, another optional example is also shown. As shown in Figs. 25 and 26, an exhaust cavity 25 is provided in an outer wall of the cylinder sleeve 20. A boss structure 29 is arranged on a cavity wall surface of the exhaust cavity 25. The exhaust port 22 penetrates from an inner wall of the cylinder sleeve 20 to the boss structure 29 and is in communication with the exhaust cavity 25. In this way, the boss structure 29 is in a form of an outward convex structure. The arrangement of the boss structure 29 advantageously reduces an opening loss of the exhaust valve plate of the exhaust valve assembly caused by viscosity of lubricating oil.
Further, as shown in Fig. 26, a thickness of the boss structure 29 in an extension direction of the exhaust port 22 is M, and 0.05 mm ≤ M ≤ 3 mm. In this way, on one hand, the thickness of the cylinder sleeve wall at the exhaust port 22 is increased to guarantee sufficient strength of the cylinder sleeve wall at the exhaust port. On the other hand, the opening loss of the exhaust valve plate of the exhaust valve assembly can be reduced.
In the present application, as shown in Fig. 27, a sectional area of a cross section of each slide block 40 in a sliding direction of the slide block is S. as shown in Fig. 22, the assembly eccentricity of the cross groove structure 30 is e. According to the operation principle of the compressor, it can be obtained that the volume of the single volume-variable cavity 311 is V1 = 4eS, a working volume of the entire compressor is V, and V= 4V1 =16eS, that is, the displacement V of the compressor is 16eS in cubic millimeter.
In the present application, as shown in Figs. 23 and 41, an area of a hole section of the exhaust port 22 is S1, a volume of the single volume-variable cavity 311 is V1, and 750 ≤ V1/S1 ≤ 3300. In this way, by reasonably optimizing a ratio range of the volume V1 of the single volume-variable cavity 311 to the area S1 of the hole section of the exhaust port 22, it is guaranteed that the area S1 of the hole section of the exhaust port 22 falls within a reasonable range, a situation that the exhaust loss is increased due to a large exhaust rate caused by the too small exhaust port 22 is avoided, and a large clearance volume (see Fig. 41) caused by the too large exhaust port 22 is also avoided. The unit of V1 is cubic millimeter, and the unit of S1 is square millimeter.
Coefficient of performance (COP) in Fig. 41 refers to a ratio of a cooling capacity or heating capacity of the compressor to power consumption of the compressor, and is a parameter reflecting performance and energy saving of the compressor.
In the present application, the value range of the ratio V1/S1 is a ratio of numerical values without units.
As shown in Figs. 2 and 19, a longitudinal section of the inclined notch 27 through a diameter of the cylinder sleeve 20 coincides with a longitudinal section of the exhaust port 22 through the diameter of the cylinder sleeve 20. Specifically, as shown in Fig. 19, the inclined notch 27 is arranged at a position in an angle range of (arccos (2R/B) - 2 * arccos 2R/B) in a circumferential direction of the cylinder sleeve 20. R is a radius of an inner circle of the cylinder sleeve 20, and B is a distance between the two relatively parallel straight line segments of the axial projection of the slide block 40 in the through hole 41. In this way, by reasonably optimizing the position of the inclined notch 27 arranged in the circumferential direction of the cylinder sleeve 20, overcompression or undercompression of the compressor can be avoided. The angle range of β in Fig. 19 is (arccos (2R/B) - 2 * arccos 2R/B), that is, the inclined notch 27 can be arranged within the above range in the circumferential direction of the cylinder sleeve 20.
As shown in Fig. 20, an inclined direction of the inclined notch 27 extends from an end surface of one axial end of the cylinder sleeve 20 to an axis of the cylinder sleeve 20, an included angle between the inclined notch 27 and the end surface of the cylinder sleeve 20 is α, and 15° ≤ α ≤ 60°. In this way, the exhaust loss is reduced advantageously, thereby improving the performance of the compressor. Furthermore, the inclined notch 27 can guide air flow. However, the inclined notch 27 increases a clearance of the compressor, and then the performance of the compressor is reduced. Since air encounters resistance and loss when flowing, the included angle α between the inclined notch 27 and the end surface of the cylinder sleeve 20 can be reasonably optimized to find an optimal point between an air flow loss and increasing the clearance.
As shown in Fig. 20, an equivalent diameter of a circle in which the inclined notch 27 is located is D, a volume of the single volume-variable cavity 311 is V1, and 400 ≤ V1/D ≤ 1000. The unit of D is mm. In this way, the exhaust noise is reduced advantageously as much as possible. By reasonably optimizing the equivalent diameter D of the circle where the inclined notch 27 is located, a value of V1/D can satisfy: 400 ≤ V1/D ≤ 1000. An optimal point is found between reducing the air flow loss and increasing the clearance.
In the present application, the value range of the ratio V1/ D is a ratio of numerical values without units.
As shown in Fig. 21, an area of a hole section of the first axial exhaust port 22 is S4, a volume of the single volume-variable cavity 311 is V1, and 750 ≤ V1/S4 ≤ 3300. In this way, a balance between the exhaust loss and the clearance volume is taken into account to guarantee that the COP of the compressor can be optimized.
In the present application, the value range of the ratio V1/S4 is a ratio of numerical values without units.
As shown in Fig. 21, an area of a hole section of the second axial exhaust port 22 is S2, a volume of the single volume-variable cavity 311 is V1, and 50 ≤ V1/S2 ≤ 250. In this way, a balance between the exhaust loss and the clearance volume is taken into account to guarantee that the COP of the compressor can be optimized.
In the present application, the value range of the ratio V1/S2 is a ratio of numerical values without units.
As shown in Figs. 2, 10-20, 22 and 24, the cylinder sleeve 20 has one radial suction hole 21 and a suction cavity 23. The suction cavity 23 is in communication with the radial suction hole 21. In this way, it is guaranteed that a large amount of air can be stored in the suction cavity 23, such that the variable volume cavities 311 can fully suck the air, and then the compressor can suck enough air. When air suction is insufficient, the stored air can be supplied to the variable volume cavities 311 in time, so as to guarantee compression efficiency of the compressor.
In some embodiments, the suction cavity 23 is a cavity formed by radially hollowing out the inner wall surface of the cylinder sleeve 20. One suction cavity 23 may be provided, and alternatively, two suction cavities with one above the other may also be provided.
Specifically, the suction cavity 23 extends by a first preset distance around the circumferential direction of the inner wall surface of the cylinder sleeve 20 to form an arc suction cavity 23. In this way, it is guaranteed that a volume of the suction cavity 23 is large enough to store a large amount of air.
As shown in Figs. 2, 10-20, 22 and 24, two suction cavities 23 are provided. The two suction cavities 23 are spaced in the axial direction of the cylinder sleeve 20. The cylinder sleeve 20 further has a suction communication cavity 24. The two suction cavities 23 are in communication with the suction communication cavity 24, and the radial suction hole 21 is in communication with the suction cavities 23 through the suction communication cavity 24. Thus, the volume of the suction cavities 23 can be increased, and suction pressure pulsation is reduced.
Further, as shown in Fig. 2, the suction communication cavity 24 extends by a second preset distance in the axial direction of the cylinder sleeve 20. At least one end of the suction communication cavity 24 penetrates the axial end surface of the cylinder sleeve 20. In this way, it is convenient to form the suction communication cavity 24 from the end surface of the cylinder sleeve 20, and machining convenience of the suction communication cavity 24 is guaranteed.
In the example, as shown in Fig. 2, an exhaust port 22 is provided in a side wall of the cylinder sleeve 20 close to the lower flange 53, an inclined notch 27 is formed on an inner circle of an end of the cylinder sleeve 20 facing the upper flange 52, and moreover, the upper flange 52 is provided with a first axial exhaust hole 511 and a second axial exhaust hole 512. The exhaust port 22 is in communication with the second axial exhaust hole 512 through the exhaust cavity 25 and the communication hole 26. The inclined notch 27 is in communication with the first axial exhaust hole 511.

Example 2

Differences between the example and Example 1 lie in that, as shown in Fig. 28, an exhaust port 22 is provided in a side wall of a cylinder sleeve 20 close to an upper flange 52, an inclined notch 27 is formed on an inner circle of an end of the cylinder sleeve 20 facing an lower flange 53, moreover, the lower flange 53 is provided with a first axial exhaust hole 511, and the upper flange 52 is provided with a second axial exhaust hole 512. The exhaust port 22 is in communication with the second axial exhaust hole 512 through an exhaust cavity 25 and a communication hole 26. The inclined notch 27 is in communication with the first axial exhaust hole 511.

Example 3

Differences between the example and Example 1 lie in that, as shown in Fig. 29, an exhaust port 22 is provided in a side wall of a cylinder sleeve 20 close to an upper flange 52, an inclined notch 27 is formed on an inner circle of an end of the cylinder sleeve 20 facing an lower flange 53, and moreover, the lower flange 53 is provided with a first axial exhaust hole 511 and a second axial exhaust hole 512. The exhaust port 22 is in communication with the second axial exhaust hole 512 through an exhaust cavity 25 and a communication hole 26. The inclined notch 27 is in communication with the first axial exhaust hole 511.

Example 4

Differences between the example and Example 1 lie in that, as shown in Fig. 30, an exhaust port 22 is provided in a side wall of a cylinder sleeve 20 close to an upper flange 52, an inclined notch 27 is formed on an inner circle of an end of the cylinder sleeve 20 facing the upper flange 52, an exhaust port 22 is provided in a side wall of the cylinder sleeve 20 close to the lower flange 53, an inclined notch 27 is formed on an inner circle of an end of the cylinder sleeve 20 facing the lower flange 53, and moreover, the upper flange 52 and the lower flange 53 are each provided with a first axial exhaust hole 511 and a second axial exhaust hole 512. The exhaust port 22 on an upper side of the cylinder sleeve 20 is in communication with the second axial exhaust hole 512 on the upper flange 52 through an exhaust cavity 25 and a communication hole 26, and the inclined notch 27 on an upper end surface of the cylinder sleeve 20 is in communication with the first axial exhaust hole 511 on the upper flange 52. The exhaust port 22 on a lower side of the cylinder sleeve 20 is in communication with the second axial exhaust hole 512 on the lower flange 53 through the exhaust chamber 25 and the communication hole 26, and the inclined notch 27 on a lower end surface of the cylinder sleeve 20 is in communication with the first axial exhaust hole 511 on the lower flange 53.

Example 5

Differences between the example and Example 1 lie in that, as shown in Fig. 31, a cylinder sleeve 20 has two radial suction holes 21, the two radial suction holes 21 are spaced in an axial direction of the cylinder sleeve 20, and the two radial suction holes 21 are respectively in communication with suction cavities 23 at corresponding sides.

Example 6

Differences between the example and Example 2 lie in that, as shown in Fig. 32, a cylinder sleeve 20 has two radial suction holes 21, the two radial suction holes 21 are spaced in an axial direction of the cylinder sleeve 20, and the two radial suction holes 21 are respectively in communication with suction cavities 23 at corresponding sides.

Example 7

Differences between the example and Example 3 lie in that, as shown in Fig. 33, a cylinder sleeve 20 has two radial suction holes 21, the two radial suction holes 21 are spaced in an axial direction of the cylinder sleeve 20, and the two radial suction holes 21 are respectively in communication with suction cavities 23 at corresponding sides.

Example 8

Differences between the example and Example 4 lie in that, as shown in Fig. 34, a cylinder sleeve 20 has two radial suction holes 21, the two radial suction holes 21 are spaced in an axial direction of the cylinder sleeve 20, and the two radial suction holes 21 are respectively in communication with suction cavities 23 at corresponding sides.
Certainly, in an example not shown in the drawings of the present application, suction may be performed by means of the flanges 50, specifically, the upper flange 52 and the lower flange 53. Alternatively, one flange 50 of the two flanges 50 may be used for suction in combination with the cylinder sleeve 20.
It should be noted that the terms used herein are for the purpose of describing detailed embodiments merely and are not intended to limit the illustrative embodiments in accordance with the present application. As used herein, the singular form is also intended to include the plural form unless clearly indicated otherwise in the context. Moreover, it should also be understood that the terms "encompass" and/or "comprise" and "include" used in the description specify the presence of features, steps, operations, devices, assemblies, and/or their combinations.
The relative arrangement of components and steps, numerical expressions, and numerical values set forth in these examples do not limit the scope of the present application unless specifically stated otherwise. Moreover, it should be understood that the dimensions of all portions shown in the accompanying drawings are not drawn to actual scale for ease of description. Techniques, methods, and apparatuses known to those of ordinary skill in the art may not be discussed in detail, but where appropriate, should be deemed as part of the granted description. In all instances shown and discussed herein, any particular value should be interpreted as merely being illustrative instead of being restrictive. Therefore, other instances in the illustrative examples can have different values. It should be noted that similar numerals and letters denote similar items in the following accompanying drawings. Thus, once a certain item is defined in one accompanying drawing, it is not required to be discussed further in subsequent accompanying drawings.
For ease of description, the spatially-relative terms such as "on", "above", "on the upper surface", and "on the upper portion" can be used herein to describe the spatial position relation between one device or feature and another device or feature as shown in the figures. It should be understood that the spatially-relative terms are intended to encompass different orientations in use or operation except for the orientation of the device described in the figures. For example, if the device in the accompanying drawings is inverted, a device described as "above another device or configuration" or "on another device or configuration" will then be located as "below another device or configuration" or "underneath another device or configuration". Therefore, the illustrative term "above" can indicate two orientations "above" and "below". The device can also be located in other different ways (being rotated by 90 degrees or in another orientation), and the spatially-relative descriptions used herein are interpreted correspondingly.
It should be noted that the terms used herein are for the purpose of describing detailed embodiments merely and are not intended to limit the illustrative embodiments in accordance with the present application. As used herein, the singular is intended to include the plural unless the context clearly dictates. Furthermore, it is to be understood that the terms "include" and/or "comprise" used in this specification specify the presence of features, steps, works, devices, components, and/or their combinations.
The terms "first", "second" and so forth, in the specification and claims of the present application and in the above-mentioned drawings, are used to distinguish between similar objects, instead of necessarily describing a particular order or sequential order. It should be understood that the data used in this way may be interchanged where appropriate, such that the embodiments of the present application described herein can be implemented in other sequences than those illustrated or described herein.
All technical features in the above examples can be combined with one another randomly. In order to make the description concise, not all possible combinations of all the technical features in the above examples are described. However, as long as there is no contradiction between the combinations of these technical features, the combinations should be deemed as falling within the scope of description in the description.
The above examples merely express several embodiments of the present application, and their descriptions are specific and detailed, but should not be interpreted as limiting the scope of the present application patent. It should be noted that those of ordinary skill in the art can also make several variations and improvements without departing from the concept of the present application, and these variations and improvements fall within the scope of protection of the present application. Therefore, the scope of protection of the present application patent should be defined by the appended claims.

Claims

A fluid machine, comprising:
a crankshaft (10), wherein the crankshaft (10) is provided with two eccentric portions (11) in an axial direction of the crankshaft;

a cylinder sleeve (20), wherein the crankshaft (10) and the cylinder sleeve (20) are disposed in an eccentric manner with a fixed eccentric distance;

a cross groove structure (30), wherein the cross groove structure (30) is rotatably disposed in the cylinder sleeve (20), the cross groove structure (30) has two limiting channels (31), the two limiting channels (31) are sequentially disposed in the axial direction of the crankshaft (10), and an extension direction of the limiting channels (31) is perpendicular to the axial direction of the crankshaft (10);

slide blocks (40), wherein each of the slide blocks (40) has a through hole (41), two slide blocks (40) are provided, the two eccentric portions (11) correspondingly extend into two through holes (41) of the two slide blocks (40), the two slide blocks (40) are correspondingly slidably disposed in the two limiting channels (31) to form a volume-variable cavity (311), the volume-variable cavity (311) is located in a slide direction of the slide blocks (40), and the crankshaft (10) rotates to drive the two slide blocks (40) to interact with the cross groove structure (30) while reciprocating in the two limiting channels (31) in a sliding manner, such that the cross groove structure (30) and the slide blocks (40) rotate in the cylinder sleeve (20); and

two flanges (50), wherein the two flanges (50) are disposed at two axial ends of the cylinder sleeve (20) respectively, at least one flange (50) of the two flanges (50) is provided with a first axial exhaust hole (511), and at least one flange (50) of the two flanges (50) is provided with a second axial exhaust hole (512); wherein

an inclined notch (27) is provided at an edge of an inner circle of at least one of the two axial ends of the cylinder sleeve (20), the inclined notch (27) is in communication with the first axial exhaust hole (511), at least one exhaust port (22) is provided on a side wall surface of the cylinder sleeve (20), and the exhaust port (22) is in communication with the second axial exhaust hole (512).
The fluid machine according to claim 1, wherein the first axial exhaust hole (511) and the second axial exhaust hole (512) in a flange (50) are on a same radius of the flange (50), and the second axial exhaust hole (512) is located on an outer peripheral side of the first axial exhaust hole (511).
The fluid machine according to claim 1, wherein a flange (50) at one end of the cylinder sleeve (20) having the inclined notch (27) is provided with the first axial exhaust hole (511), and the inclined notch (27) is disposed opposite the first axial exhaust hole (511).
The fluid machine according to claim 3, wherein a geometric center line of the first axial exhaust hole (511) passes through a geometric center of the inclined notch (27).
The fluid machine according to claim 1, wherein
a projection of the each of the slide blocks (40) in a slide direction of the each of the slide blocks is a part of a semicircle; and/or,

an axial projection of the each of the slide block (40) in the through hole (41) has two relatively parallel straight line segments and an arc segment connecting ends of the two straight line segments, and

the exhaust port (22) is disposed at a position in an angle range of (arccos (2R/B) - 2 * arccos (2R/B)) in a circumferential direction of the cylinder sleeve (20), wherein R is a radius of an inner circle of the cylinder sleeve (20), and B is a distance between the two relatively parallel straight line segments of the axial projection of the each of the slide blocks (40) in the through hole (41).
The fluid machine according to claim 1, wherein
an exhaust cavity (25) is provided in an outer wall of the cylinder sleeve (20), the exhaust port (22) is in communication with the exhaust cavity (25) from an inner wall of the cylinder sleeve (20), the fluid machine further comprises an exhaust valve assembly, and the exhaust valve assembly is disposed in the exhaust cavity (25) and corresponds to the exhaust port (22); and

a communication hole (26) is further provided in an axial end surface of the cylinder sleeve (20), the communication hole (26) is in communication with the exhaust cavity (25), and the communication hole (26) is in communication with the second axial exhaust hole (512).
The fluid machine according to claim 6, wherein a distance between a plane where one end of the exhaust port (22) in communication with the exhaust cavity (25) and an axis of the cylinder sleeve (20) is K, a radius of an inner circle of the cylinder sleeve (20) is R, and 1 mm ≤ K - R ≤ 5 mm.
The fluid machine according to claim 6, wherein a cavity sectional area of the exhaust cavity (25) in an axial direction of the cylinder sleeve (20) is S3, a height of the exhaust cavity (25) in the axial direction of the cylinder sleeve (20) is N, a displacement of the fluid machine is V, and 0.2 ≤ (N * S3)/V ≤ 5.
The fluid machine according to claim 1, wherein an exhaust cavity (25) is provided in an outer wall of the cylinder sleeve (20), a boss structure (29) is disposed on a cavity wall surface of the exhaust cavity (25), and the exhaust port (22) penetrates from an inner wall of the cylinder sleeve (20) to the boss structure (29) and is in communication with the exhaust cavity (25).
The fluid machine according to claim 9, wherein a thickness of the boss structure (29) in an extension direction of the exhaust port (22) is M, and 0.05 mm ≤ M ≤ 3 mm.
The fluid machine according to claim 1, wherein an area of a hole section of the exhaust port (22) is S1, a volume of the volume-variable cavity (311) is V1, and 750 ≤ V1/S1 ≤ 3300.
The fluid machine according to claim 1, wherein an inclined direction of the inclined notch (27) extends from an end surface of one axial end of the cylinder sleeve (20) to an axis of the cylinder sleeve (20), an included angle between the inclined notch (27) and the end surface of the cylinder sleeve (20) is α, and 15° ≤ α ≤ 60°.
The fluid machine according to claim 1, wherein an equivalent diameter of a circle in which the inclined notch (27) is located is D, a volume of the volume-variable cavity (311) is V1, and 400 ≤ V1/D ≤ 1000.
The fluid machine according to claim 1, wherein a longitudinal section of the inclined notch (27) through a diameter of the cylinder sleeve (20) coincides with a longitudinal section of the exhaust port (22) through the diameter of the cylinder sleeve (20).
The fluid machine according to claim 1, wherein
an area of a hole section of the first axial exhaust port (22) is S4, a volume of the single volume-variable cavity (311) is V1, and 750 ≤ V1/S4 ≤ 3300; and/or

an area of a hole section of the second axial exhaust port (22) is S2, a volume of the single volume-variable cavity (311) is V1, and 50 ≤ V1/S2 ≤ 250.
The fluid machine according to claim 6, wherein the exhaust cavity (25) penetrates to an outer wall surface of the cylinder sleeve (20), the fluid machine further comprises an exhaust cover plate (70), and the exhaust cover plate (70) is connected with the cylinder sleeve (20) and seals the exhaust cavity (25).
The fluid machine according to any one of claims 1-16, wherein a phase difference of a first included angle (A) exists between the two eccentric portions (11), eccentric amounts of the two eccentric portions (11) are equal, a phase difference of a second included angle (B) exists between the extension directions of the two limiting channels (31), and the first angle (A) is twice of the second angle (B).
The fluid machine according to claim 17, wherein the first included angle (A) is 160°-200°, and the second included angle (B) is 80°-100°.
The fluid machine according to any one of claims 1-18, wherein the each of the slide blocks (40) has a pressing surface (42) facing an end of the limiting channel (31), and a projected area S_{slide block} of the pressing surface (42) in the slide direction of the slide blocks (40) and an area S_exhaust of the exhaust port (22) of the cylinder sleeve (20) satisfy that a value of S_{slide block}/S_exhaust is 8-25.
A heat exchange apparatus, comprising a fluid machine, wherein the fluid machine is the fluid machine according to any one of claims 1-19.