CN117145772A

CN117145772A - Fluid machine and heat exchange device

Info

Publication number: CN117145772A
Application number: CN202210565528.8A
Authority: CN
Inventors: 于瑞波; 杜忠诚; 张培林; 李直; 任丽萍; 杨春霞
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: WO2023226413A1

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, and the two sliding blocks are correspondingly arranged in the two limiting channels in a sliding manner and form a variable volume cavity; the two flanges are respectively arranged at the two axial ends of the cylinder sleeve, one of the two flanges is provided with an air inlet channel, the cylinder sleeve is provided with a radial air suction hole, and the air inlet channel and the radial air suction hole are respectively communicated with the two variable-volume cavities. The invention solves the problems of low energy efficiency, high noise and insufficient air suction 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 conventional compressor has a phenomenon of insufficient suction, and suction loss increases due to the insufficient suction.

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 insufficient air suction 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, wherein the crankshaft is provided with two eccentric portions in an axial direction thereof; the crankshaft and the cylinder sleeve are eccentrically arranged, and the eccentric distance is fixed; the 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 the two axial ends of the cylinder sleeve, one of the two flanges is provided with an air inlet channel, the cylinder sleeve is provided with a radial air suction hole, and the air inlet channel and the radial air suction hole are respectively communicated with the two variable-volume cavities.

Further, the ratio S/V of the cross-sectional area S of the hole cross-section of the intake passage to the displacement V of the fluid machine is in the range of 0.001 to 0.6; the ratio S1/S between the sectional area S1 of the hole section of the radial suction hole and the sectional area S of the hole section of the intake passage is in the range of 0.2 to 3.

Further, the inner wall surface of the cylinder sleeve is provided with two air suction cavities which are arranged at intervals along the axial direction of the cylinder sleeve, the air inlet channel is communicated with the variable-volume cavity through the air suction cavities at the corresponding sides in the two air suction cavities, and the radial air suction holes are communicated with the variable-volume cavity through the air suction cavities at the corresponding sides in the two air suction cavities.

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

Further, the air inlet channel comprises a radial channel section and an axial channel section which are sequentially communicated, the cylinder sleeve is further provided with an air suction communication cavity, the air suction communication cavity is only communicated with the air suction cavity which is communicated with the air inlet channel, the air suction communication cavity extends a second preset distance along the axial direction of the cylinder sleeve, and one end of the air suction communication cavity penetrates through the axial end face of the cylinder sleeve and is communicated with the axial channel section.

Further, the air inlet channel comprises a radial channel section and an axial channel section which are sequentially communicated, the cylinder sleeve is further provided with an air suction communication cavity, the two air suction cavities are communicated with the air suction communication cavity, the air suction communication cavity extends a third preset distance along the axial direction of the cylinder sleeve, and one end of the air suction communication cavity penetrates through the axial end face of the cylinder sleeve and is communicated with the axial channel section.

Further, the position of the radial channel section in the circumferential direction of the flange coincides with the position of the radial suction hole in the circumferential direction of the cylinder liner.

Further, the channel diameter D of the radial channel section is equal to the hole diameter D1 of the radial suction hole.

Further, the channel diameter D of the radial channel section is not equal to the hole diameter D1 of the radial suction hole.

Further, the channel diameter D of the radial channel section and the skirt height H of the flange satisfy: and is more than or equal to 0.5mm.

Further, the hole diameter D1 of the radial air suction hole and the axial height H1 of the cylinder sleeve satisfy the following conditions: and is more than or equal to 0.5mm.

Further, exhaust channels are formed in the end faces of the two flanges, and the two exhaust channels are respectively communicated with the variable-volume cavities on the corresponding sides.

Further, the tail end of the radial air suction hole is a first compression air inlet, the tail end of the air inlet channel is a second compression air inlet, the initial ends of the two air exhaust channels are compression air exhaust ports, when the sliding block positioned at the corresponding side of the radial air suction hole is positioned at the air inlet position, the first compression air inlet is communicated with the corresponding variable volume cavity, and when the sliding block positioned at the corresponding side of the radial air suction hole is positioned at the air exhaust position, the corresponding variable volume cavity is communicated with the compression air exhaust port at the corresponding side; when the sliding block positioned at the corresponding side of the air inlet channel is positioned at the air inlet position, the second compression air inlet is communicated with the corresponding variable volume cavity, and when the sliding block positioned at the corresponding side of the air inlet channel is positioned at the air outlet position, the corresponding variable volume cavity is communicated with the compression air outlet at the corresponding side.

Further, the fluid machine is a compressor.

Further, the tail end of the radial air suction hole is a first expansion air outlet, the tail end of the air inlet channel is a second expansion air outlet, the initial ends of the two air outlet channels are expansion air inlets, when the sliding block positioned at the corresponding side of the radial air suction hole is positioned at the air inlet position, the first expansion air outlet is communicated with the corresponding variable volume cavity, and when the sliding block positioned at the corresponding side of the radial air suction hole is positioned at the air outlet position, the corresponding variable volume cavity is communicated with the expansion air inlet at the corresponding side; when the sliding block positioned at the corresponding side of the air inlet channel is positioned at the air inlet position, the second expansion air outlet is communicated with the corresponding variable volume cavity, and when the sliding block positioned at the corresponding side of the air inlet channel is positioned at the air outlet position, the corresponding variable volume cavity is communicated with the expansion air inlet at the corresponding side.

Further, the fluid machine is an expander.

Further, an exhaust cavity is formed in the outer wall of the cylinder sleeve, the cylinder sleeve is further provided with an exhaust port, the exhaust port is communicated to the exhaust cavity through the inner wall of the cylinder sleeve, and the fluid machine further comprises an exhaust valve assembly which is arranged in the exhaust cavity and corresponds to the exhaust port.

Further, the exhaust ports are two, the two exhaust ports are arranged at intervals along the axial direction of the cylinder sleeve, the exhaust valve assemblies are two groups, and the two groups of exhaust valve assemblies are respectively arranged corresponding to the two exhaust ports.

Further, a communication hole is further formed in at least one axial end face of the cylinder sleeve, the communication hole is communicated with the exhaust cavity, an exhaust channel is formed in a flange opposite to the communication hole in the two flanges, and the communication hole is communicated with the exhaust channel.

Further, the exhaust port is one and is communicated with the variable volume cavity at the corresponding side, and at least one axial end face of the cylinder sleeve is also provided with a communication hole which is communicated with the exhaust cavity; a first exhaust channel is arranged on a flange opposite to the communication hole in the two flanges, and the communication hole is communicated with the first exhaust channel; the flange far away from the exhaust port of the two flanges is provided with a second exhaust passage which is communicated with the variable-volume cavity at the corresponding side.

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

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

Further, the fluid machine is a compressor.

Further, the tail end of the radial air suction hole is a first expansion air outlet, the tail end of the air inlet channel is a second expansion air outlet, the air outlet on the cylinder sleeve is an expansion air inlet, when the sliding block positioned at the corresponding side of the radial air suction hole is positioned at the air inlet position, the first expansion air outlet is communicated with the corresponding volume cavity, and when the sliding block positioned at the corresponding side of the radial air suction hole is positioned at the air outlet position, the corresponding volume cavity is communicated with the expansion air inlet at the corresponding side; when the sliding block positioned at the corresponding side of the air inlet channel is positioned at the air inlet position, the second expansion air outlet is communicated with the corresponding variable volume cavity, and when the sliding block positioned at the corresponding side of the air inlet channel is positioned at the air outlet position, the corresponding variable volume cavity is communicated with the expansion air inlet at the corresponding side.

Further, the fluid machine is an expander.

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 adopting the technical scheme of the application, the air inlet channel is arranged on one of the two flanges, the radial air suction hole is arranged on the cylinder sleeve, and the air inlet channel and the radial air suction hole are respectively communicated with the two variable volume cavities, so that the air suction reliability of the fluid machinery is ensured, the air suction loss of the fluid machinery caused by insufficient air suction is avoided, and the volume efficiency of the fluid machinery is ensured to be optimal.

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 is a schematic view showing an internal structure of a fluid machine according to a first embodiment of the present application;

FIG. 2 shows a schematic structural view of a pump body assembly of the fluid machine 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. 3;

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 shows a schematic structural view of the upper flange of the pump body assembly of FIG. 3;

FIG. 11 shows a schematic cross-sectional structural view of the upper flange of FIG. 10;

FIG. 12 shows a schematic structural view of a cylinder liner of the pump body assembly of FIG. 3;

FIG. 13 shows a schematic cross-sectional structural view of the cylinder liner of FIG. 12;

FIG. 14 shows a schematic cross-sectional structural view of the cylinder liner of FIG. 12 from another perspective;

FIG. 15 shows a schematic view of the upper flange and cylinder liner of the pump body assembly of FIG. 2 in a non-self-contained intake configuration;

fig. 16 is a schematic view showing an internal structure of a fluid machine according to a second embodiment of the present invention;

FIG. 17 shows a schematic view of the pump body assembly of the fluid machine of FIG. 16;

FIG. 18 shows an exploded view of the pump body assembly of FIG. 16;

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

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

FIG. 21 shows a schematic view of the lower flange of FIG. 18;

FIG. 22 shows a schematic cross-sectional structural view of the lower flange of FIG. 21;

FIG. 23 shows a schematic view of the lower flange and cylinder liner of the pump body assembly of FIG. 17 in a non-self-contained intake configuration;

FIG. 24 shows a schematic view of the upper and lower flange vents of the pump body assembly of FIG. 17;

FIG. 25 shows a schematic structural view of cylinder liner side exhaust of the pump body assembly of FIG. 17;

FIG. 26 shows a schematic diagram of a combination cylinder liner side exhaust and flange exhaust of the pump body assembly of FIG. 17;

FIG. 27 shows a graph of the effect of the ratio of the cross-sectional area of the bore section of the intake passage to the displacement of the fluid machine on the volumetric efficiency of the compressor;

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 shows a schematic view of the principle of the mechanism of operation of the compressor of fig. 31, in which the center of the limit groove structure and the center of the eccentric portion coincide.

Wherein the above figures include the following reference numerals:

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

20. cylinder sleeve; 21. 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;

30. a cross slot structure; 31. a limiting channel;

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

50. a flange; 51. an exhaust passage; 511. a first exhaust passage; 512. a second exhaust passage; 52. an upper flange; 53. a lower flange; 54. an air intake passage; 541. a radial channel section; 542. an axial channel section;

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 segment O ₁ O ₂ Is the midpoint O of (1) ₀ As a virtual center, a problem of deterioration of high-frequency vibration characteristics of a compressor due to failure to provide a balance system, based on the principle of the above-described operation mechanism, as shown in fig. 31, a method of using O ₀ As a means ofThe movement of the centre of the drive shaft, i.e. the centre of the cylinder 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 to form a variable-volume cavity, the variable-volume cavity is located 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, 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 eccentric part 11 with the maximum driving torque can normally drive the corresponding sliding block 40 to rotate, the cross groove structure 30 is driven to rotate through the sliding block 40, the sliding block 40 at the dead point position is driven to continuously rotate through the cross groove structure 30, the reliability of mechanical lifting and stability of the operation of the fluid is realized, and the reliability of the operation and the reliability of the fluid movement 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 the two eccentric parts is equal to the eccentric amount of the second eccentric part 11 corresponding to the crankshaft 10, and the eccentric amount is equal to the axis O of the crankshaft 10 ₀ With the axis O of the cross slot structure 30 ₁ Eccentric distance between them, the crankshaft 10 rotates to drive the second slider 40 to do circular motion, and the second slider 40 interacts with the cross slot structure 30 andsliding reciprocally within the spacing 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. 28, 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 The revolution angular velocity of the slider 40 is the same as the rotation angular velocity of the eccentric portion 11.

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

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

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

In 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.

As shown in fig. 1 to 15, 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. 1 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. 1 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. 1 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. 1 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.

In the present application, the cross groove structure 30 has a center hole through which the two limiting passages 31 communicate, and the center hole has a larger diameter than 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.

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

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 arranged first sliding surfaces in sliding contact with the slide 40, the slide 40 has a second sliding surface cooperating with the first sliding surfaces, the slide 40 has a pressing surface 42 facing the end of the limiting channel 31, the pressing surface 42 acts as the head of the slide 40, the two second sliding surfaces are connected by the pressing surface 42, and the pressing surface 42 faces the variable volume chamber. 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 exhaust port 22 with 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.

Further, as shown in fig. 1, the dispenser part 80 has two air suction pipes therein for communicating with the radial air suction holes 21 and the air intake passage 54, respectively.

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 this 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 a variable volume cavity, the pump body assembly 83 has 4 variable volume cavities in total, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 circles, and a single variable volume cavity 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.

Aiming at solving the problem of insufficient air suction of a compressor, the invention supplements the following matters on the basis of the fluid machinery, and the concrete matters are as follows:

example 1

As shown in fig. 1 to 15, the fluid machine further includes two flanges 50, the two flanges 50 being disposed at axial ends of the cylinder liner 20, respectively, one of the two flanges 50 having an intake passage 54, the cylinder liner 20 having a radial suction hole 21, the intake passage 54 and the radial suction hole 21 communicating with the two variable volume chambers, respectively.

By arranging the air inlet channel 54 on one flange 50 of the two flanges 50 and simultaneously arranging the radial air suction holes 21 on the cylinder sleeve 20, the air inlet channel 54 and the radial air suction holes 21 are respectively communicated with the two variable volume cavities, so that the air suction reliability of the fluid machinery is ensured, the air suction loss of the fluid machinery caused by insufficient air suction is avoided, and the volume efficiency of the fluid machinery is ensured to be optimal.

In addition, the air inlet channel 54 and the radial air suction holes 21 are respectively arranged on the flange 50 and the cylinder sleeve 20, so that the air suction of the compressor is ensured to be sufficient, the performance and the refrigerating capacity of the compressor are improved, the problem that various structures interfere with each other in design due to small size is solved, and the design of the compressor is easier.

In the present embodiment, the upper flange 52 is provided with an air inlet channel 54.

Preferably, the ratio S/V of the cross-sectional area S of the hole cross-section of the intake passage 54 to the displacement V of the fluid machine is in the range of 0.001 to 0.6; the ratio S1/S between the sectional area S1 of the hole cross section of the radial suction hole 21 and the sectional area S of the hole cross section of the intake passage 54 is in the range of 0.2 to 3. In this way, by reasonably optimizing the range of the ratio S/V of the cross-sectional area S of the hole section of the radial suction hole 21 to the displacement V of the fluid machine, it is advantageous to reduce the suction loss and the suction shortage due to the compressor, thereby improving the performance of the compressor.

Fig. 27 is a graph showing the effect of the ratio of the cross-sectional area of the hole cross-section of the intake passage 54 to the displacement V of the fluid machine on the volumetric efficiency of the compressor. From the figure, it can be seen that the volumetric efficiency of the compressor is optimal when the S/V is within the range of 0.001 to 0.6.

As shown in fig. 2, 13 and 15, the inner wall surface of the cylinder liner 20 has two air suction chambers 23, the two air suction chambers 23 are arranged at intervals along the axial direction of the cylinder liner 20, the air inlet passage 54 communicates with the variable volume chamber through the air suction chamber 23 on the corresponding side of the two air suction chambers 23, and the radial air suction hole 21 communicates with the variable volume chamber through the air suction chamber 23 on the corresponding side of the two air suction chambers 23. In this way, it is ensured that the suction chamber 23 can store a large amount of gas so that the variable volume chamber can be filled with suction gas, thereby enabling the suction gas to be sufficient, and when the suction gas is insufficient, the stored gas can be timely supplied to the variable volume chamber 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 and 11, the intake passage 54 includes a radial passage section 541 and an axial passage section 542 which are sequentially communicated, the cylinder liner 20 further has an intake communication chamber 24, the intake communication chamber 24 communicates only with the intake chamber 23 for communicating with the intake passage 54, the intake communication chamber 24 extends a second predetermined distance in the axial direction of the cylinder liner 20, and one end of the intake communication chamber 24 penetrates through an axial end face of the cylinder liner 20 and communicates with the axial passage section 542. In this way, the air suction reliability of the air inlet passage 54 is ensured, and meanwhile, the purpose of independently sucking air from the air inlet passage 54 and the radial air suction holes 21 of the cylinder sleeve 20 is realized, so that the air suction processes of the air inlet passage 54 and the radial air suction holes 21 are ensured not to interfere with each other.

As shown in fig. 15, the intake passage 54 includes a radial passage section 541 and an axial passage section 542 that are sequentially communicated, the cylinder liner 20 further has an intake communication chamber 24, both intake chambers 23 are communicated with the intake communication chamber 24, the intake communication chamber 24 extends a third preset distance in the axial direction of the cylinder liner 20, and one end of the intake communication chamber 24 penetrates through the axial end face of the cylinder liner 20 and communicates with the axial passage section 542. In this way, the air suction reliability of the air inlet passage 54 is ensured, and meanwhile, the purpose of independent air suction of the air inlet passage 54 and the radial air suction holes 21 of the cylinder sleeve 20 is realized.

When the displacement of the upper and lower portions of the cylinder liner 20 is not equal, the intake may be performed by the non-independent intake in fig. 15, so that the intake of the compressor is ensured to be sufficient.

As shown in fig. 3, the radial passage segments 541 are located at positions in the circumferential direction of the flange 50 that coincide with the positions of the radial suction holes 21 in the circumferential direction of the cylinder liner 20.

As shown in fig. 11 and 13, the channel diameter D of the radial channel section 541 is equal to the hole diameter D1 of the radial suction hole 21.

Of course, the channel diameter D of the radial channel section 541 and the hole diameter D1 of the radial suction hole 21 may also be unequal.

As shown in fig. 11, the channel diameter D of the radial channel section 541 and the skirt height H of the flange 50 satisfy: H/2-D/2 is more than or equal to 0.5mm. In this way, the flange 50 is ensured to have sufficient structural strength while ensuring that the compressor is suction-sufficient.

As shown in fig. 13, the hole diameter D1 of the radial intake holes 21 and the axial height H1 of the cylinder liner 20 satisfy: H1/2-D1/2 is more than or equal to 0.5mm. In this way, the cylinder liner 20 is ensured to have sufficient structural strength while ensuring that the compressor is adequately suctioned.

Example two

It should be noted that, in this embodiment, as shown in fig. 16 to 23, the lower flange 53 in this embodiment is provided with an air inlet channel 54, and the other features are similar, and are not described herein.

As shown in fig. 23, the intake passage 54 and the radial intake holes 21 of the cylinder liner 20 are non-independent air-intake, and when the displacement of the upper and lower portions of the cylinder liner 20 is not equal, air-intake can be performed by the non-independent air-intake method shown in fig. 23, thereby ensuring sufficient air intake of the compressor.

The following describes the discharge of the compressor by taking the compressor in the second embodiment as an example:

in the first embodiment, the upper flange 52 and the lower flange 53 perform flange exhaust:

as shown in fig. 24, the end surfaces of the two flanges 50 are each provided with an exhaust passage 51, and the two exhaust passages 51 are respectively communicated with the variable volume chambers on the corresponding sides. In this way, the two exhaust passages 51 are respectively arranged on the planes of the upper flange 52 and the lower flange 53, but not on the curved surface of the side wall of the cylinder sleeve 20, so that the processing and manufacturing difficulty of the exhaust passages 51 is greatly reduced.

Taking a compressor as an example, the tail end of the radial air suction hole 21 is a first compression air inlet, the tail end of the air inlet channel 54 is a second compression air inlet, the initial ends of the two air exhaust channels 51 are compression air outlets, when the sliding block 40 positioned at the corresponding side of the radial air suction hole 21 is positioned at the air inlet position, the first compression air inlet is communicated with the corresponding variable volume cavity, and when the sliding block 40 positioned at the corresponding side of the radial air suction hole 21 is positioned at the air exhaust position, the corresponding variable volume cavity is communicated with the compression air outlet at the corresponding side; the second compression intake port is in communication with the corresponding variable volume chamber when the slider 40 on the corresponding side of the intake passage 54 is in the intake position, and the corresponding variable volume chamber is in communication with the corresponding compression exhaust port when the slider 40 on the corresponding side of the intake passage 54 is in the exhaust position.

Other use occasions: the compressor can be used as an expander by exchanging positions of the first compression air inlet, the second compression air inlet and the compression air outlet. That is, the compression exhaust port of the compressor is used as the expansion machine air intake port, high-pressure air is introduced, the other pushing mechanism rotates, and the air is discharged through the first compression air inlet (first expansion exhaust port) and the second compression air inlet (second expansion exhaust port) of the compressor after expansion.

Specifically, the radial suction holes 21 are provided with a first expansion exhaust port at the end, the air inlet channel 54 is provided with a second expansion exhaust port at the end, the initial ends of the two air outlet channels 51 are expansion air inlets, when the sliding block 40 positioned at the corresponding side of the radial suction holes 21 is positioned at the air inlet position, the first expansion exhaust port is communicated with the corresponding variable volume cavity, and when the sliding block 40 positioned at the corresponding side of the radial suction holes 21 is positioned at the air outlet position, the corresponding variable volume cavity is communicated with the expansion air inlet at the corresponding side; the second expansion exhaust port is in communication with the corresponding variable volume chamber when the slider 40 on the corresponding side of the intake passage 54 is in the intake position, and the corresponding variable volume chamber is in communication with the corresponding expansion intake port when the slider 40 on the corresponding side of the intake passage 54 is in the exhaust position.

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

Further, the expansion exhaust chamber extends around the circumference of the inner wall surface of the cylinder liner 20 by a first preset distance to form an arc expansion exhaust chamber, and the expansion exhaust chamber extends from the expansion exhaust port to the side where the expansion air inlet is located, and the extending direction of the expansion exhaust chamber is in the same direction as the rotating direction of the cross groove structure 30.

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

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

In the second exhaust embodiment, the cylinder liner 20 side exhaust:

as shown in fig. 25, the outer wall of the cylinder sleeve 20 is provided with an exhaust cavity 25, the cylinder sleeve 20 is further provided with an exhaust port 22, the exhaust port 22 is communicated to the exhaust cavity 25 by the inner wall of the cylinder sleeve 20, and the fluid machine further comprises an exhaust valve assembly which is arranged in the exhaust cavity 25 and corresponds to the exhaust port 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. 25, the exhaust ports 22 are two, the two exhaust ports 22 are arranged at intervals along the axial direction of the cylinder sleeve 20, the exhaust valve assemblies are two groups, and the two groups of exhaust valve assemblies are respectively arranged corresponding to the two exhaust ports 22. Thus, as the two exhaust ports 22 are respectively provided with two groups of exhaust valve assemblies, a large amount of gas in the variable-volume cavity is effectively prevented from leaking, and the compression efficiency of the variable-volume cavity is ensured.

As shown in fig. 25, a communication hole 26 is further provided on at least one axial end surface of the cylinder liner 20, the communication hole 26 communicates with the exhaust chamber 25, an exhaust passage 51 is provided on a flange 50 opposite to the communication hole 26 of the two flanges 50, and the communication hole 26 communicates with the exhaust passage 51. In this way, the exhaust reliability of the cylinder liner 20 is ensured.

In this embodiment, the upper flange 52 is provided with the exhaust passage 51, however, the lower flange 53 may be provided with the exhaust passage 51, or even the upper flange 52 and the lower flange 53 may be provided with the exhaust passage 51, which may be selected as desired.

Exhaust embodiment three, cylinder liner 20 side exhaust incorporates one of two flanges 50:

as shown in fig. 26, the exhaust port 22 is one, and the exhaust port 22 is communicated with the variable volume chamber on the corresponding side, and a communication hole 26 is further arranged on at least one axial end surface of the cylinder sleeve 20, and the communication hole 26 is communicated with the exhaust chamber 25; a first exhaust passage 511 is formed in a flange 50 opposite to the communication hole 26 in the two flanges 50, and the communication hole 26 is communicated with the first exhaust passage 511; the flange 50 on the side of the two flanges 50 remote from the exhaust port 22 has a second exhaust passage 512, and the second exhaust passage 512 communicates with the variable volume chamber on the corresponding side. In this way, the purpose of exhausting the cylinder liner 20 side and exhausting one end face of the two flanges 50 is achieved, and the exhaust reliability of the compressor is ensured.

In the present application, 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 functions to isolate the variable volume chamber from the external space of the pump body assembly 83.

Taking a compressor as an example, the tail end of the radial air suction hole 21 is a first compression air inlet, the tail end of the air inlet channel 54 is a second compression air inlet, the air outlet 22 on the cylinder sleeve 20 is a compression air outlet, when the sliding block 40 positioned on the corresponding side of the radial air suction hole 21 is positioned at the air inlet position, the first compression air inlet is communicated with the corresponding variable volume cavity, and when the sliding block 40 positioned on the corresponding side of the radial air suction hole 21 is positioned at the air outlet position, the corresponding variable volume cavity is communicated with the compression air outlet on the corresponding side; the second compression intake port is in communication with the corresponding variable volume chamber when the slider 40 on the corresponding side of the intake passage 54 is in the intake position, and the corresponding variable volume chamber is in communication with the corresponding compression exhaust port when the slider 40 on the corresponding side of the intake passage 54 is in the exhaust position.

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

Specifically, the end of the radial air suction hole 21 is a first expansion air outlet, the end of the air inlet channel 54 is a second expansion air outlet, the air outlet 22 on the cylinder sleeve 20 is an expansion air inlet, when the sliding block 40 positioned at the corresponding side of the radial air suction hole 21 is positioned at the air inlet position, the first expansion air outlet is communicated with the corresponding variable volume cavity, and when the sliding block 40 positioned at the corresponding side of the radial air suction hole 21 is positioned at the air outlet position, the corresponding variable volume cavity is communicated with the expansion air inlet at the corresponding side; the second expansion exhaust port is in communication with the corresponding variable volume chamber when the slider 40 on the corresponding side of the intake passage 54 is in the intake position, and the corresponding variable volume chamber is in communication with the corresponding expansion intake port when the slider 40 on the corresponding side of the intake passage 54 is in the exhaust position.

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 invention unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.

Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

It should be noted that the terms "first," "second," and the like in the description and 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, the variable volume cavity is positioned 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 cylinder sleeve comprises two flanges (50), wherein the two flanges (50) are respectively arranged at two axial ends of the cylinder sleeve (20), one of the two flanges (50) is provided with an air inlet channel (54), the cylinder sleeve (20) is provided with a radial air suction hole (21), and the air inlet channel (54) and the radial air suction hole (21) are respectively communicated with the two variable-volume cavities.

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

the ratio S/V of the cross-sectional area S of the hole cross-section of the air inlet channel (54) to the displacement V of the fluid machine is in the range of 0.001-0.6;

the ratio S1/S between the cross-sectional area S1 of the hole cross-section of the radial air suction hole (21) and the cross-sectional area S of the hole cross-section of the air inlet channel (54) is in the range of 0.2-3.

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

the inner wall surface of the cylinder sleeve (20) is provided with two air suction cavities (23), the two air suction cavities (23) are arranged at intervals along the axial direction of the cylinder sleeve (20), the air inlet channel (54) is communicated with the variable-volume cavity through the air suction cavities (23) at the corresponding sides of the two air suction cavities (23), and the radial air suction holes (21) are communicated with the variable-volume cavity through the air suction cavities (23) at the corresponding sides of the two air suction cavities (23).

4. A fluid machine according to claim 3, wherein the suction chamber (23) extends a first predetermined distance around the circumference of the inner wall surface of the cylinder liner (20) to form an arc-shaped suction chamber (23).

5. A fluid machine according to claim 3, wherein the intake passage (54) comprises a radial passage section (541) and an axial passage section (542) which are sequentially communicated, the cylinder liner (20) further has an intake communication chamber (24), the intake communication chamber (24) communicates only with the intake chamber (23) for communicating with the intake passage (54), the intake communication chamber (24) extends a second predetermined distance in the axial direction of the cylinder liner (20), and one end of the intake communication chamber (24) penetrates an axial end face of the cylinder liner (20) and communicates with the axial passage section (542).

6. A fluid machine according to claim 3, wherein the intake passage (54) comprises a radial passage section (541) and an axial passage section (542) which are sequentially communicated, the cylinder liner (20) further has an intake communication chamber (24), both of the intake chambers (23) are communicated with the intake communication chamber (24), the intake communication chamber (24) extends a third preset distance in the axial direction of the cylinder liner (20), and one end of the intake communication chamber (24) penetrates through an axial end face of the cylinder liner (20) and communicates with the axial passage section (542).

7. A fluid machine according to claim 5 or 6, characterized in that the position of the radial channel section (541) in the circumferential direction of the flange (50) coincides with the position of the radial suction hole (21) in the circumferential direction of the cylinder liner (20).

8. A fluid machine according to claim 5 or 6, characterized in that the channel diameter D of the radial channel section (541) is equal to the hole diameter D1 of the radial suction hole (21).

9. A fluid machine according to claim 5 or 6, characterized in that the channel diameter D of the radial channel section (541) is not equal to the hole diameter D1 of the radial suction hole (21).

10. A fluid machine according to claim 5 or 6, characterized in that the channel diameter D of the radial channel section (541) and the skirt height H of the flange (50) satisfy between: (H/2-D/2) is more than or equal to 0.5mm.

11. The fluid machine according to claim 5 or 6, characterized in that between the hole diameter D1 of the radial suction holes (21) and the axial height H1 of the cylinder liner (20) is satisfied: (H1/2-D1/2) is more than or equal to 0.5mm.

12. The fluid machine according to claim 1, wherein the end surfaces of both flanges (50) are provided with exhaust passages (51), and both exhaust passages (51) are respectively communicated with the variable-volume chambers on the corresponding sides.

13. The fluid machine according to claim 12, wherein the radial suction holes (21) are terminated by a first compression intake, the intake channels (54) are terminated by a second compression intake, the initial ends of both the exhaust channels (51) are compression exhaust,

when the sliding block (40) positioned at the corresponding side of the radial air suction hole (21) is positioned at an air inlet position, the first compression air inlet is communicated with the corresponding variable volume cavity, and when the sliding block (40) positioned at the corresponding side of the radial air suction hole (21) is positioned at an air outlet position, the corresponding variable volume cavity is communicated with the compression air outlet at the corresponding side;

the second compression intake port is in communication with the corresponding variable volume chamber when the slider (40) on the corresponding side of the intake passage (54) is in an intake position, and the corresponding variable volume chamber is in communication with the compression exhaust port on the corresponding side when the slider (40) on the corresponding side of the intake passage (54) is in an exhaust position.

14. The fluid machine of claim 13, wherein the fluid machine is a compressor.

15. The fluid machine according to claim 12, wherein the radial suction holes (21) are terminated with a first expansion exhaust port, the intake passages (54) are terminated with a second expansion exhaust port, the initial ends of both the exhaust passages (51) are expansion intake ports,

When the sliding block (40) positioned at the corresponding side of the radial air suction hole (21) is positioned at an air inlet position, the first expansion air outlet is communicated with the corresponding variable volume cavity, and when the sliding block (40) positioned at the corresponding side of the radial air suction hole (21) is positioned at an air outlet position, the corresponding variable volume cavity is communicated with the expansion air inlet at the corresponding side;

the second expansion exhaust port is in communication with the corresponding variable volume chamber when the slider (40) on the corresponding side of the intake passage (54) is in an intake position, and the corresponding volume chamber is in communication with the expansion intake port on the corresponding side when the slider (40) on the corresponding side of the intake passage (54) is in an exhaust position.

16. The fluid machine of claim 12, wherein the fluid machine is an expander.

17. The fluid machine according to claim 1, wherein an exhaust cavity (25) is formed in an outer wall of the cylinder sleeve (20), the cylinder sleeve (20) is further provided with an exhaust port (22), the exhaust port (22) is communicated to the exhaust cavity (25) by an inner wall of the cylinder sleeve (20), and the fluid machine further comprises an exhaust valve assembly, and the exhaust valve assembly is arranged in the exhaust cavity (25) and corresponds to the exhaust port (22).

18. The fluid machine of claim 17, wherein the number of exhaust ports (22) is two, the two exhaust ports (22) are arranged at intervals along the axial direction of the cylinder sleeve (20), the number of exhaust valve assemblies is two, and the two exhaust valve assemblies are respectively arranged corresponding to the two exhaust ports (22).

19. The fluid machine according to claim 18, wherein a communication hole (26) is further provided on at least one axial end surface of the cylinder liner (20), the communication hole (26) is communicated with the exhaust cavity (25), an exhaust passage (51) is provided on the flange (50) opposite to the communication hole (26) in the two flanges (50), and the communication hole (26) is communicated with the exhaust passage (51).

20. The fluid machine of claim 17, wherein the fluid machine is further configured to,

the exhaust port (22) is one, the exhaust port (22) is communicated with the variable-volume cavity at the corresponding side, a communication hole (26) is further formed in at least one axial end face of the cylinder sleeve (20), and the communication hole (26) is communicated with the exhaust cavity (25);

a first exhaust passage (511) is formed in the flange (50) opposite to the communication hole (26) in the two flanges (50), and the communication hole (26) is communicated with the first exhaust passage (511); the flange (50) of the two flanges (50) on the side remote from the exhaust port (22) has a second exhaust passage (512), the second exhaust passage (512) communicating with the variable volume chamber on the corresponding side.

21. The fluid machine according to claim 17, 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).

22. Fluid machine according to any of claims 17 to 21, characterized in that the radial suction holes (21) end in a first compression intake, the intake channels (54) end in a second compression intake, the exhaust ports (22) on the cylinder liners (20) are compression exhaust ports,

23. The fluid machine of claim 22, wherein the fluid machine is a compressor.

24. Fluid machine according to any of claims 17 to 21, characterized in that the radial suction holes (21) end in a first expansion exhaust port, the intake channels (54) end in a second expansion exhaust port, the exhaust ports (22) on the cylinder liners (20) are expansion intake ports,

25. The fluid machine of claim 24, wherein the fluid machine is an expander.

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

27. 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 26.