WO2023103871A1

WO2023103871A1 - Fluid machine and heat exchange device

Info

Publication number: WO2023103871A1
Application number: PCT/CN2022/135921
Authority: WO
Inventors: 魏会军; 杜忠诚; 宋雪威; 任丽萍; 李直; 张培林; 于瑞波
Original assignee: 珠海格力电器股份有限公司
Priority date: 2021-12-07
Filing date: 2022-12-01
Publication date: 2023-06-15
Also published as: CN116241472A

Abstract

A fluid machine and a heat exchange device. The fluid machine comprises a crankshaft (10), a cylinder sleeve (20), at least one end cover (100), a crossed groove structure (30), and sliding blocks (40); a first included angle A is formed between two eccentric portions (11) of the crankshaft (10); the crankshaft (10) and the cylinder sleeve (20) are eccentrically arranged, and an eccentric distance is fixed; the crankshaft (10) passes through the end cover (100), and is arranged together with the cylinder sleeve (20); two limiting channels (31) of the crossed groove structure (30) are sequentially arranged in the axial direction of the crankshaft (10); the extension direction of each limiting channel (31) is perpendicular to the axial direction of the crankshaft (10); a second included angle B is formed between the extension directions of the two limiting channels (31); the first included angle A is twice the second included angle B; at least one supporting protruding ring (36) is arranged in the axial direction of the crossed groove structure (30); the outer circle diameter of the supporting protruding ring (36) is smaller than the outer circle diameter of the crossed groove structure (30); the supporting protruding ring (36) protrudes towards the end cover (100); a through hole (41) is formed on each sliding block (40); there are two sliding blocks (40); and the two eccentric portions (11) correspondingly extend into the two through holes (41) of the two sliding blocks (40).

Description

Fluid Machinery and Heat Exchange Equipment

Cross References to Related Applications

This application is based on the application with CN application number 202111512372.9 and the application date is December 7, 2021, and claims its priority. The disclosure content of this CN application is hereby incorporated into this application as a whole.

technical field

The present disclosure relates to the technical field of heat exchange systems, in particular, to fluid machinery and heat exchange equipment.

Background technique

Fluid machines in the related art include compressors, expanders, and the like.

Taking compressors as an example, according to energy saving and environmental protection and consumers' requirements for air-conditioning comfort, the air-conditioning industry has been pursuing high efficiency and low noise. As the heart of the air conditioner, the compressor has a direct impact on the energy efficiency and noise level of the air conditioner. As the mainstream household air-conditioning compressor, the rolling rotor compressor has been relatively mature after nearly a hundred years of development. Due to the limitation of structural principles, the optimization space is limited. In order to achieve a major breakthrough, it is necessary to innovate from the structural principle.

Therefore, it is necessary to propose a fluid machine such as a compressor and an expander with the characteristics of high energy efficiency and low noise.

Contents of the invention

According to one aspect of the present disclosure, a fluid machine is provided, including a crankshaft, a cylinder liner, at least one end cover, a cross groove structure, and a slider, wherein the crankshaft is provided with two eccentric parts along its axial direction, and the two eccentric parts There is a phase difference of the first angle A between them; the crankshaft and the cylinder liner are set eccentrically and the eccentric distance is fixed; the crankshaft is set through the end cover and the cylinder liner; the cross groove structure is rotatably set in the cylinder liner, and the cross groove structure has two Two limiting channels are arranged in sequence along the axial direction of the crankshaft, the extending direction of the limiting channels is perpendicular to the axial direction of the crankshaft, and there is a second included angle B between the extending directions of the two limiting channels Phase difference, wherein, the first included angle A is twice the second included angle B, there is at least one supporting protruding ring in the axial direction of the intersecting groove structure, and the outer diameter of the supporting protruding ring is smaller than the outer diameter of the intersecting groove structure, The supporting convex ring protrudes toward the end cover; the slider has two through holes, and the two eccentric parts correspondingly extend into the two through holes of the two sliders, and the two sliders are correspondingly slidably arranged at two limits. The variable volume chamber is located in the sliding direction of the slider. The crankshaft rotates to drive the slider to reciprocate in the limiting channel and interact with the intersecting groove structure, so that the intersecting groove structure and the slider Rotate in the cylinder liner.

In some embodiments, the end cover includes a flange and a limiting plate, the flange is arranged at the end of the cylinder liner, the limiting plate is arranged between the flange and the cylinder liner, and the limiting plate has a through hole for avoiding the crankshaft , the height of the supporting convex ring is greater than the thickness of the limit plate, the end surface of the supporting convex ring facing the flange side serves as a thrust surface, and the supporting convex ring passes through the through hole and is in thrust contact with the flange.

In some embodiments, the height of the supporting convex ring and the thickness of the limiting plate meet: the height difference between the two ranges from 0.05 mm to 1 mm.

In some embodiments, the end cover includes a flange and a limiting plate, the flange is arranged at the end of the cylinder liner, the limiting plate is arranged between the flange and the cylinder liner, and the limiting plate has a through hole for avoiding the crankshaft , the supporting convex ring extends into the through hole and is set, the height of the supporting convex ring is smaller than the thickness of the limiting plate, and the supporting ring surface outside the supporting convex ring with the intersecting groove structure is in thrust contact with the limiting plate.

In some embodiments, the limiting plate is arranged concentrically with the intersecting groove structure, and the through hole is a central hole of the limiting plate.

In some embodiments, only one end of the intersecting groove structure has a supporting convex ring, wherein, the end surface of the end of the intersecting groove structure that is not provided with a supporting convex ring is only reserved with an opening for the crankshaft to protrude, and the opening and the supporting convex ring Concentrically arranged, the opening communicates with the limiting channel; or, the end surface of the end of the intersecting groove structure that is not provided with a supporting convex ring is open, and the limiting channel directly passes through the end surface along the axial direction of the intersecting groove structure.

In some embodiments, both ends of the intersecting groove structure have supporting convex rings. Along the axial direction of the intersecting groove structure, the inner ring of the supporting convex ring faces the middle of the intersecting groove structure and penetrates to form a channel for the crankshaft to pass through. The supporting convex ring is arranged concentrically, and the channel communicates with the limiting channel.

In some embodiments, the crankshaft is concentric with the flange.

In some embodiments, there is a first assembly gap between the crankshaft and the flange, and the range of the first assembly gap is 0.005mm˜0.05mm.

In some embodiments, the range of the first assembly gap is 0.01-0.03 mm.

In some embodiments, the eccentricity of the eccentric part is equal to the assembly eccentricity of the crankshaft and the cylinder liner.

In some embodiments, both ends of the limiting channel penetrate to the outer peripheral surface of the intersecting groove structure.

In some embodiments, the two sliders are arranged concentrically with the two eccentric parts respectively, and the sliders make circular motions around the axis of the crankshaft. There is a first rotation gap between the wall of the through hole and the eccentric parts, and the first rotation gap The range is 0.005mm ~ 0.05mm.

In some embodiments, the intersecting groove structure is arranged coaxially with the cylinder liner, and there is a second rotation gap between the outer peripheral surface of the intersecting groove structure and the inner wall surface of the cylinder liner, and the size of the second rotation gap is 0.005mm-0.1mm.

In some embodiments, the first included angle A is 160°-200°; the second included angle B is 80°-100°.

In some embodiments, the eccentric portion has an arc surface, and the central angle of the arc surface is greater than or equal to 180 degrees.

In some embodiments, the eccentric portion is cylindrical.

In some embodiments, the proximal end of the eccentric portion is flush with the outer circle of the shaft portion of the crankshaft; or, the proximal end of the eccentric portion protrudes from the outer circle of the shaft portion of the crankshaft; or, the proximal end of the eccentric portion is located on the crankshaft The inner side of the outer circle of the shaft body part.

In some embodiments, the two eccentric portions are arranged at intervals in the axial direction of the crankshaft.

In some embodiments, the intersecting groove structure has a central hole through which the two limiting passages communicate, and the diameter of the central hole is larger than the diameter of the crankshaft shaft body.

In some embodiments, the diameter of the central hole is larger than the diameter of the eccentric portion.

In some embodiments, the position-limiting channel has a set of opposite first sliding surfaces that are in sliding contact with the slider, the slider has a second sliding surface that cooperates with the first sliding surfaces, and the slider has a The extrusion surface at the end of the channel serves as the head of the slider, the two second sliding surfaces are connected through the extrusion surface, and the extrusion surface faces the variable volume cavity.

In some embodiments, the extrusion surface is an arc surface, and the distance between the arc center of the arc surface and the center of the through hole is equal to the eccentricity of the eccentric portion.

In some embodiments, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner; or, there is a difference between the radius of curvature of the arc surface and the radius of the inner circle of the cylinder liner, and the difference ranges from -0.05mm to 0.025 mm.

In some embodiments, the difference ranges from -0.02 to 0.02mm.

In some embodiments, the shape of the slider on the cross-section of the limiting channel matches the shape of the cross-section of the limiting channel.

In some embodiments, the cylinder liner has a compression intake port and a compression exhaust port. When any slider is in the intake position, the compression intake port is connected to the corresponding variable volume cavity; In the case of the air position, the corresponding variable volume chamber is connected to the compression exhaust port.

In some embodiments, the projected area of the extrusion surface in the sliding direction of the slider is the S _slider , the exhaust area of the compression exhaust port of the cylinder liner is the S _row , and the value of the S _slider /S _row is 8 to 25. .

In some embodiments, the value of S _slider /S _row is 12-18.

In some embodiments, the inner wall of the cylinder liner has an air suction chamber, and the air suction chamber communicates with the compressed air inlet.

In some embodiments, the suction cavity extends a first preset distance around the inner wall surface of the cylinder liner to form an arc-shaped suction cavity.

In some embodiments, there are two suction cavities, the two suction cavities are arranged at intervals along the axial direction of the cylinder liner, the cylinder liner also has a suction communication cavity, both of the two suction cavities communicate with the suction communication cavity, and The compressed air inlet communicates with the suction cavity through the suction communication cavity.

In some embodiments, the suction communication cavity extends a second preset distance along the axial direction of the cylinder liner, and at least one end of the suction communication cavity passes through the axial end surface of the cylinder liner.

In some embodiments, an exhaust cavity is opened on the outer wall of the cylinder liner, and the compressed exhaust port is connected to the exhaust cavity by the inner wall of the cylinder liner. The fluid machine also includes an exhaust valve assembly, which is arranged on the exhaust The cavity is set correspondingly to the compression exhaust port.

In some embodiments, there are two compression exhaust ports, and the two compression exhaust ports are arranged at intervals along the axial direction of the cylinder liner. There are two sets of exhaust valve assemblies, and the two sets of exhaust valve assemblies correspond to two compression exhaust port settings.

In some embodiments, a communication hole is provided on the axial end surface of the cylinder liner, and the communication hole communicates with the exhaust chamber. The end cover includes a flange and a limiting plate. It is arranged between the flange and the cylinder liner, the flange is provided with an exhaust passage, the position where the limit plate is opposite to the exhaust passage is provided with an avoidance passage, and the communication hole communicates with the exhaust passage through the avoidance passage.

In some embodiments, the exhaust cavity penetrates to the outer wall of the cylinder liner, and the fluid machine further includes an exhaust cover plate, which is connected with the cylinder liner and seals the exhaust cavity.

In some embodiments, the fluid machine is a compressor.

In some embodiments, the cylinder liner has an expansion exhaust port and an expansion intake port. When any slider is in the intake position, the expansion exhaust port is connected to the corresponding variable volume chamber; In the case of the air position, the corresponding variable volume chamber is connected to the expansion air inlet.

In some embodiments, the inner wall of the cylinder liner has an expansion exhaust cavity, and the expansion exhaust cavity communicates with the expansion exhaust port.

In some embodiments, the expansion exhaust cavity extends a first preset distance around the inner wall surface of the cylinder liner to form an arc-shaped expansion exhaust cavity, and the expansion exhaust cavity extends from the expansion exhaust port to the expansion intake The side where the port is located extends, and the extension direction of the expansion exhaust cavity is in the same direction as the rotation direction of the intersecting groove structure.

In some embodiments, there are two expansion exhaust chambers, and the two expansion exhaust chambers are arranged at intervals along the axial direction of the cylinder liner. The communication cavity communicates, and the expansion exhaust port communicates with the expansion exhaust cavity through the expansion exhaust communication cavity.

In some embodiments, the expansion exhaust communication cavity extends a second preset distance along the axial direction of the cylinder liner, and at least one end of the expansion exhaust communication cavity passes through the axial end surface of the cylinder liner.

In some embodiments, the fluid machine is an expander.

According to another aspect of the present disclosure, a heat exchange device is provided, including a fluid machine, and the fluid machine is the above-mentioned fluid machine.

Applying the technical solution of the present disclosure, by setting the intersecting groove structure into a structural form with two limiting channels, and correspondingly setting two sliders, the two eccentric parts of the crankshaft correspondingly extend into the two through holes of the two sliders At the same time, the two sliders are correspondingly slidably arranged in the two limiting passages to form a variable volume cavity. Since the first angle A between the two eccentric parts is the first angle A between the extension directions of the two limiting passages Two times the included angle B, so that when one of the two sliders is at the dead point position, that is, the driving torque of the eccentric part corresponding to the slider at the dead point position is 0, and it is at the dead point position The slider at the position cannot continue to rotate, and at this time the driving torque of the other eccentric part of the two eccentric parts driving the corresponding slider is the maximum value, ensuring that the eccentric part with the largest driving torque can normally drive the corresponding slider Rotate, so that the cross groove structure is driven to rotate through the slider, and then the slider at the dead point is driven to continue to rotate through the cross groove structure, realizing the stable operation of the fluid machine, avoiding the dead point position of the movement mechanism, and lifting It improves the motion reliability of the fluid machinery, thus ensuring the working reliability of the heat exchange equipment.

In addition, according to the calculation formula of the friction power consumption of the outer circle of the intersecting groove structure, the friction power consumption of the friction pair is proportional to the power of the radius. Therefore, the smaller the radius of the friction pair, the smaller the friction power consumption.

Specifically, the axial direction of the intersecting groove structure of this embodiment has at least one supporting protruding ring, and at the same time, the outer diameter of the supporting protruding ring is smaller than the outer diameter of the intersecting groove structure, and the supporting protruding ring protrudes toward the end cover. In this way, due to The diameter of the outer circle of the supporting convex ring is significantly smaller than the diameter of the outer circle of the intersecting groove structure. During the operation of the compressor, the outer circle of the supporting convex ring is used as a bearing surface, so that the friction power consumption is significantly smaller than that of the outer circle of the intersecting groove structure as a bearing surface.

Furthermore, since the fluid machinery provided by the present application can run stably, that is, fluid machinery such as compressors and expanders can be ensured to have high energy efficiency and low noise, thereby ensuring the reliability of the heat exchange equipment.

Description of drawings

The accompanying drawings constituting a part of the present application are used to provide a further understanding of the present disclosure, and the exemplary embodiments and descriptions of the present disclosure are used to explain the present disclosure, and do not constitute undue limitations on the present disclosure. In the attached picture:

Fig. 1 shows a schematic diagram of a mechanism principle of compressor operation according to an optional embodiment of the present disclosure;

Fig. 2 shows a schematic diagram of the principle of operation of the compressor in Fig. 1;

FIG. 3 shows a schematic diagram of the internal structure of a compressor according to Embodiment 1 of the present disclosure;

Fig. 4 shows a schematic structural view of the pump body assembly of the compressor in Fig. 3;

Figure 5 shows a schematic diagram of the exploded structure of the pump body assembly in Figure 4;

Fig. 6 shows the schematic diagram of the assembly structure of crankshaft, intersecting groove structure, slide block in Fig. 5;

Fig. 7 shows the schematic cross-sectional structure diagram of the crankshaft, the intersecting groove structure and the slide block in Fig. 6;

FIG. 8 shows a schematic structural diagram of the cross-groove structure in FIG. 5;

Fig. 9 shows a schematic structural view of the slider in Fig. 5;

Fig. 10 shows a schematic structural view of the intersecting groove structure in Fig. 5 and two limiting plates in an assembled state;

Fig. 11 shows a schematic structural view of the shaft body part and two eccentric parts of the crankshaft in Fig. 5;

Fig. 12 shows a structural schematic diagram of the shaft body part of the crankshaft in Fig. 11 and the eccentricity of the two eccentric parts;

Fig. 13 shows a schematic cross-sectional structural view of the assembly eccentricity of the crankshaft and cylinder liner in Fig. 3;

Fig. 14 shows a schematic structural view of the cylinder liner, the limiting plate and the lower flange in Fig. 5 when they are in an exploded state;

Fig. 15 shows a schematic structural view of the eccentricity between the cylinder liner and the limiting plate in Fig. 14;

Fig. 16 shows a schematic structural view of the slider in Fig. 9 in the axial direction of the through hole;

Figure 17 shows a schematic structural view of the cylinder liner in Figure 14;

Fig. 18 shows a structural schematic diagram of another viewing angle of the cylinder liner in Fig. 17;

Fig. 19 shows a schematic cross-sectional structural view of the cylinder liner in Fig. 18;

Fig. 20 shows a schematic cross-sectional structural view of another viewing angle of the cylinder liner in Fig. 17;

FIG. 21 shows a schematic structural view of the Y-direction viewing angle in FIG. 20;

Fig. 22 shows a cross-sectional schematic view of the upper flange, two limiting plates and the cylinder liner in Fig. 13 from another perspective, in which the exhaust path of the pump body assembly is shown;

Fig. 23 shows a schematic cross-sectional structural view of the exhaust path of the pump body assembly in Fig. 3;

Fig. 24 shows a schematic structural view of the cylinder liner and exhaust cover in Fig. 5 when they are in an exploded state;

Fig. 25 shows a schematic diagram of the state structure of the compressor in Fig. 3 at the beginning of suction;

Fig. 26 shows a schematic diagram of the state structure of the compressor in Fig. 3 in the suction process;

Fig. 27 shows a schematic diagram of the state structure of the compressor in Fig. 3 at the end of suction;

Figure 28 shows a schematic view of the state structure of the compressor in Figure 3 when it is compressing gas;

Fig. 29 shows a schematic diagram of the state structure of the compressor in Fig. 3 in the exhaust process;

Fig. 30 shows a schematic diagram of the state structure of the compressor in Fig. 3 at the end of exhaust;

Fig. 31 shows a schematic diagram of the structure of the intersecting groove structure in Fig. 3 and the cross section of the slider being elliptical;

Fig. 32 shows a schematic diagram of the structure of the intersecting groove structure and the cross section of the slider in Fig. 3;

Fig. 33 shows a schematic diagram of the intersecting groove structure in Fig. 3 and the cross-section of the slider in a trapezoidal shape;

Fig. 34 shows a schematic diagram of the structure of the intersecting groove structure in Fig. 3 and the cross section of the slider being circular;

Fig. 35 shows a schematic diagram of the internal structure of a compressor according to Embodiment 2 of the present disclosure;

Fig. 36 shows a schematic structural view of the pump body assembly of the compressor in Fig. 35;

Figure 37 shows a schematic diagram of the exploded structure of the pump body assembly in Figure 36;

Figure 38 shows a schematic diagram of the assembly structure of the crankshaft, the intersecting groove structure, and the slide block in Figure 36;

Fig. 39 shows a schematic cross-sectional structural view of the crankshaft, intersecting groove structure, and slider in Fig. 38;

FIG. 40 shows a schematic structural diagram of the cross-groove structure in FIG. 37;

Figure 41 shows a schematic structural view of the slider in Figure 36;

Figure 42 shows a schematic structural view of the cylinder liner and the lower flange in Figure 36 when they are in an exploded state;

Figure 43 shows a schematic structural view of the assembly eccentricity of the cylinder liner and the lower flange in Figure 42;

Figure 44 shows a schematic cross-sectional structural view of the assembly eccentricity of the crankshaft and cylinder liner in Figure 36;

Figure 45 shows a schematic cross-sectional view of the pump body assembly in Figure 36 from another perspective, in which the exhaust path of the pump body assembly is shown;

Fig. 46 shows a schematic cross-sectional structural view of the cylinder liner, upper flange and limit plate in Fig. 45;

Fig. 47 shows a schematic cross-sectional structural view of another viewing angle of the upper flange, the limiting plate and the cylinder liner in Fig. 36;

Figure 48 shows a schematic cross-sectional structural view of the pump body assembly with bearings in Figure 36, in which the bearings are located at both axial ends;

Figure 49 shows a schematic structural view of the intersecting groove structure and the bearing in Figure 48 when they are in an assembled state;

Figure 50 shows a schematic cross-sectional structural view of the pump body assembly with bearings in Figure 36, in which the bearing is located at one axial end;

Figure 51 shows a schematic cross-sectional structural view of the pump body assembly with bearings in Figure 50, in which the bearing is located at the other end in the axial direction;

Fig. 52 shows a schematic cross-sectional structural view of the pump body assembly with bearings in Fig. 36, in which the bearings are located on the circumferential outer peripheral side;

Fig. 53 shows a schematic cross-sectional structural view of the cylinder liner, intersecting groove structure and bearing in Fig. 52 when they are in an assembled state;

Fig. 54 shows a schematic diagram of the internal structure of a compressor according to Embodiment 3 of the present disclosure;

Fig. 55 shows a partial cross-sectional structural schematic diagram of the pump body assembly of the compressor in Fig. 54;

Fig. 56 shows a schematic structural view of the intersecting groove structure of the pump body assembly in Fig. 55;

Fig. 57 shows a schematic diagram of the internal structure of a compressor according to Embodiment 4 of the present disclosure;

Figure 58 shows a schematic structural view of the pump body assembly of the compressor in Figure 57;

Fig. 59 shows a schematic structural view of the intersecting groove structure of the pump body assembly in Fig. 58;

Fig. 60 shows a schematic diagram of the internal structure of a compressor according to Embodiment 5 of the present disclosure;

Figure 61 shows a schematic structural view of the pump body assembly of the compressor in Figure 60;

Fig. 62 shows a schematic structural view of the intersecting groove structure of the pump body assembly in Fig. 61;

Fig. 63 shows a schematic diagram of the mechanism principle of compressor operation in the related art;

Fig. 64 shows a schematic diagram of the mechanism principle of the improved compressor operation in the related art;

Fig. 65 shows a schematic diagram of the operating mechanism of the compressor in Fig. 64, in which the force arm of the drive shaft driving the slider to rotate is shown;

Fig. 66 shows a schematic diagram of the operating mechanism of the compressor in Fig. 64, in which the center of the limiting groove structure coincides with the center of the eccentric part.

Wherein, the above-mentioned accompanying drawings include the following reference signs:

10. Crankshaft; 11. Eccentric part; 12. Shaft part;

20. Cylinder liner; 21. Compression air inlet; 22. Compression exhaust port; 23. Suction cavity; 24. Suction connection cavity; 25. Exhaust cavity; 26. Communication hole;

30. Cross groove structure; 31. Limiting channel; 311. Variable volume cavity; 32. Center hole; 36. Supporting convex ring; 361. Thrust surface; 37. Supporting ring surface; 38. Opening hole; 39. Channel;

40. slider; 41. through hole; 42. extrusion surface;

50, flange; 51, exhaust channel; 52, upper flange; 53, lower flange;

60. Exhaust valve assembly; 61. Exhaust valve plate; 62. Valve plate baffle;

70. Exhaust cover;

80. Dispenser component; 81. Housing assembly; 82. Motor assembly; 83. Pump body assembly; 84. Upper cover assembly; 85. Lower cover assembly;

90. Fasteners;

100, end cover; 110, limit plate; 1101, via hole; 1102, avoidance channel;

200, bearing.

Detailed ways

The following will clearly and completely describe the technical solutions in the embodiments of the present disclosure with reference to the accompanying drawings in the embodiments of the present disclosure. Obviously, the described embodiments are only some of the embodiments of the present disclosure, not all of them. The following description of at least one exemplary embodiment is merely illustrative in nature and in no way intended as any limitation of the disclosure, its application or uses. Based on the embodiments in the present disclosure, all other embodiments obtained by persons of ordinary skill in the art without creative efforts fall within the protection scope of the present disclosure.

The present disclosure provides a fluid machine and heat exchange equipment to improve the problems of low energy efficiency and high noise of fluid machines such as compressors and expanders in the related art.

In the related art, as shown in Figure 63, a principle of compressor operating mechanism is proposed based on the cross slider mechanism, that is, point _O1 is used as the center of the cylinder, point _O2 is used as the center of the drive shaft, and point _O3 is used as the center of the slider , The cylinder and the drive shaft are set eccentrically, and the center O ₃ of the slider makes a circular motion on a circle with a diameter of O ₁ O ₂ .

In the above operating mechanism principle, the cylinder center O ₁ and the drive shaft center O ₂ are used as the two rotation centers of the motion mechanism, and at the same time, the midpoint O ₀ of the line segment O ₁ O ₂ is used as the virtual center of the slider center O ₃ , so that the slider While the block reciprocates relative to the cylinder, the slider also reciprocates relative to the drive shaft.

Since the midpoint O ₀ of the line segment O ₁ O ₂ is the virtual center, it is impossible to set up a balance system, resulting in the deterioration of the high-frequency vibration characteristics of the compressor. Based on the principle of the above-mentioned operating mechanism, as shown in Figure 64, a The motion mechanism with O ₀ as the drive shaft center, that is, the cylinder center O ₁ and the drive shaft center O ₀ as the two rotation centers of the motion mechanism, the drive shaft has an eccentric portion, the slider and the eccentric portion are coaxially arranged, and the drive shaft and The assembly eccentricity of the cylinder is equal to the eccentricity of the eccentric part, so that the slider center _O3 makes a circular motion with the drive shaft center _O0 as the center and _O1O0 as the radius _.

Correspondingly, a set of operating mechanisms is proposed, including a cylinder, a limit groove structure, a slider and a drive shaft, wherein the limit groove structure is rotatably arranged in the cylinder, and the cylinder and the limit groove structure are coaxially arranged, that is, The center _O1 of the cylinder is also the center of the limit groove structure, the slider reciprocates relative to the limit groove structure, the slider is coaxially assembled with the eccentric portion of the drive shaft, and the slider moves circularly around the shaft part of the drive shaft, specifically The movement process is: the drive shaft rotates, driving the slider to revolve around the center of the shaft part of the drive shaft, the slider rotates relative to the eccentric part at the same time, and the slider reciprocates in the limit groove of the limit groove structure, and pushes the limit Bitslot structure rotation.

However, as shown in Figure 65, the length of the force arm L that the drive shaft drives the slider to rotate is L=2e×cosθ×cosθ, where e is the eccentricity of the eccentric part, and θ is the line connecting O ₁ O ₀ and the slider The angle between the sliding directions in the limit slot.

As shown in Figure 66, when the center _O1 of the cylinder (that is, the center of the limit groove structure) coincides with the center of the eccentric part, the resultant force of the driving force of the drive shaft passes through the center of the limit groove structure, that is, it is applied to the limit groove structure. The torque on the groove structure is zero, and the limit groove structure cannot rotate. At this time, the motion mechanism is at the dead point and cannot drive the slider to rotate.

Based on this, this application proposes a mechanism principle of a cross groove structure with two limiting channels and double sliders, and based on this principle, a fluid machine such as a compressor and an expander is constructed. The fluid machine has high energy efficiency , low noise, the following will take the compressor as an example to introduce the compressor based on the cross-groove structure with two limiting channels and double sliders.

In order to improve the problems of low energy efficiency and high noise of fluid machines such as compressors and expanders in the related art, the present disclosure provides a fluid machine and heat exchange equipment, wherein the heat exchange equipment includes the following fluid machines.

1-62, the fluid machine in the embodiment of the present disclosure includes a crankshaft 10, a cylinder liner 20, at least one end cover 100, an intersecting groove structure 30 and a slider 40, wherein the crankshaft 10 is provided with two shafts along its axial direction. The eccentric part 11 has a phase difference of the first angle A between the two eccentric parts 11; the crankshaft 10 and the cylinder liner 20 are set eccentrically and the eccentric distance is fixed; the crankshaft 10 is set through the end cover 100 and the cylinder liner 20; the cross groove structure 30 is rotatably arranged in the cylinder liner 20, the intersecting groove structure 30 has two limiting channels 31, the two limiting channels 31 are arranged in sequence along the axial direction of the crankshaft 10, and the extending direction of the limiting channels 31 is perpendicular to the crankshaft 10 , and there is a phase difference of a second included angle B between the extension directions of the two limiting channels 31, wherein the first included angle A is twice the second included angle B, and the axial direction of the intersecting groove structure 30 There is at least one supporting convex ring 36, and the outer diameter of the supporting convex ring 36 is smaller than the outer diameter of the intersecting groove structure 30, and the supporting convex ring 36 protrudes toward the end cover 100; the slider 40 has a through hole 41, and the slider 40 is Two, the two eccentric parts 11 correspondingly extend into the two through holes 41 of the two sliders 40, and the two sliders 40 are correspondingly slidably arranged in the two limiting passages 31 and form a variable volume chamber 311, the variable volume chamber 311 is located in the sliding direction of the slider 40, and the crankshaft 10 rotates to drive the slider 40 to reciprocate and slide in the limiting channel 31 while interacting with the intersecting groove structure 30, so that the intersecting groove structure 30 and the slider 40 are in the cylinder liner 20 turn.

By setting the intersecting groove structure 30 into a structural form with two limiting channels 31 and correspondingly setting up two sliders 40, the two eccentric parts 11 of the crankshaft extend into the two through holes 41 of the two sliders 40 correspondingly. , at the same time, the two sliders 40 are correspondingly slidably arranged in the two limiting passages 31 to form a variable volume cavity 311, since the first angle A between the two eccentric parts 11 is the extension direction of the two limiting passages 31 Twice the second included angle B between them, so that when one of the two sliders 40 is at the dead point position, that is, the driving torque of the eccentric portion 11 corresponding to the slider 40 at the dead point position is 0, the slider 40 at the dead point cannot continue to rotate, and at this time, the driving torque of the other eccentric part 11 driving the corresponding slider 40 in the two eccentric parts 11 is the maximum value, ensuring the maximum driving torque. The eccentric portion 11 of the moment can normally drive the corresponding slider 40 to rotate, thereby driving the cross groove structure 30 to rotate through the slider 40, and then driving the slider 40 at the dead point to continue to rotate through the cross groove structure 30, realizing The stable operation of the fluid machinery avoids the dead point position of the motion mechanism, improves the movement reliability of the fluid machinery, and ensures the working reliability of the heat exchange equipment.

In addition, according to the calculation formula of the friction power consumption of the outer circle of the intersecting groove structure 30, the friction power consumption of the friction pair is proportional to the third power of the radius, and thus, the smaller the radius of the friction pair, the smaller the friction power consumption.

Specifically, the intersecting groove structure 30 of this embodiment has at least one supporting protrusion ring 36 in the axial direction, and at the same time, the outer diameter of the supporting protrusion ring 36 is smaller than the outer diameter of the intersecting groove structure 30, and the supporting protrusion ring 36 faces the end cap 100 In this way, since the outer diameter of the supporting convex ring 36 is significantly smaller than the outer diameter of the intersecting groove structure 30, during the operation of the compressor, the outer circle of the supporting convex ring 36 serves as a bearing surface, so that the frictional power consumption is significantly smaller than that of the intersecting groove structure. The outer circle of the structure 30 serves as a bearing surface.

It should be noted that, in this application, neither the first included angle A nor the second included angle B is zero.

As shown in Figures 1 and 2, when the above-mentioned fluid machine is in operation, the crankshaft 10 rotates around the axis O ₀ of the crankshaft 10; the intersecting groove structure 30 revolves around the axis O ₀ of the crankshaft 10, and the axis O ₀ Set eccentrically with the axis O ₁ of the intersecting groove structure 30 and the eccentric distance is fixed; the first slider 40 makes a circular motion with the axis O ₀ of the crankshaft 10 as the center of a circle, and the center O ₃ of the first slider 40 is aligned with the crankshaft The distance between the axis O0 of ₁₀ is equal to the eccentricity of the first eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentricity between the axis O0 of the crankshaft ₁₀ and the axis O1 of the intersecting groove structure ₃₀ distance, the crankshaft 10 rotates to drive the first slider 40 to make a circular motion, and the first slider 40 interacts with the intersecting groove structure 30 and slides reciprocally in the limiting channel 31 of the intersecting groove structure 30; The block 40 moves in a circle with the axis O0 of the crankshaft ₁₀ as the center, and the distance between the center _O4 of the second slider 40 and the axis _O0 of the crankshaft 10 is equal to the second eccentric part 11 corresponding to the crankshaft 10 eccentricity, and the eccentricity is equal to the eccentric distance between the axis O ₀ of the crankshaft 10 and the axis O ₁ of the intersecting groove structure 30, the crankshaft 10 rotates to drive the second slider 40 to do circular motion, and the second The slider 40 interacts with the intersecting groove structure 30 and slides reciprocally in the limiting channel 31 of the intersecting groove structure 30 .

The fluid machine operated as described above constitutes an Oldham slider mechanism, and the operation method adopts the principle of the Oldham slider mechanism, wherein the two eccentric parts 11 of the crankshaft 10 serve as the first connecting rod _L1 and the second connecting rod _L2 respectively. , the two limiting channels 31 of the intersecting groove structure 30 are respectively used as the third link L ₃ and the fourth link L ₄ , and the lengths of the first link L ₁ and the second link L ₂ are equal (please refer to FIG. 1 ).

As shown in Figure 1, there is a first included angle A between the first link _L1 and the second link _L2 , and there is a second included angle B between the third link _L3 and the fourth link _L4 , Wherein, the first included angle A is twice the second included angle B.

As shown in Figure 2, the line connecting the axis O ₀ of the crankshaft 10 and the axis O ₁ of the intersecting groove structure 30 is the line O ₀ O ₁ , and the line between the first connecting rod L ₁ and the line O ₀ O ₁ There is a third included angle C between them, and there is a fourth included angle D between the corresponding third link L ₃ and the connecting line O ₀ O ₁ , wherein the third included angle C is twice the fourth included angle D; There is a fifth included angle E between the second connecting rod L ₂ and the connecting line O ₀ O ₁ , and there is a sixth included angle F between the corresponding fourth connecting rod L ₄ and the connecting line O ₀ O ₁ , wherein the fifth included angle The angle E is twice the sixth angle F; the sum of the third angle C and the fifth angle E is the first angle A, and the sum of the fourth angle D and the sixth angle F is the second angle b.

Further, the operation method also includes that the rotational angular velocity of the slider 40 relative to the eccentric portion 11 is the same as the revolution angular velocity of the slider 40 around the axis O ₀ of the crankshaft ₁₀ ; This is the same as the rotational angular velocity of the slider 40 relative to the eccentric portion 11 .

Specifically, the axis _O0 of the crankshaft 10 corresponds to the rotation center of the first connecting rod _L1 and the second connecting rod _L2 , and the axis O1 of the intersecting groove structure ₃₀ corresponds to the third connecting rod L3 and the fourth connecting rod _L3 . The rotation center of the connecting rod _L4 ; the two eccentric parts 11 of the crankshaft 10 are respectively used as the first connecting rod _L1 and the second connecting rod _L2 , and the two limiting channels 31 of the intersecting groove structure 30 are respectively used as the third connecting rod L ₃ and the fourth connecting rod L ₄ , and the lengths of the first connecting rod L ₁ and the second connecting rod L ₂ are equal, so that when the crankshaft 10 rotates, the eccentric part 11 on the crankshaft 10 drives the corresponding slider 40 around the crankshaft The axis O0 of ₁₀ revolves, and the slider 40 can rotate relative to the eccentric part 11 at the same time, and the relative rotation speed of the two is the same, because the first slider 40 and the second slider 40 are respectively in two corresponding limits Reciprocating movement in the position channel 31, and drives the intersecting groove structure 30 to make a circular motion, limited by the two limiting channels 31 of the intersecting groove structure 30, the moving direction of the two sliders 40 always has the phase of the second included angle B difference, when one of the two sliders 40 is at the dead center position, the eccentric portion 11 for driving the other of the two sliders 40 has the largest driving torque, and the eccentric portion 11 with the largest driving torque can Normally drive the corresponding slider 40 to rotate, so that the cross groove structure 30 is driven to rotate by the slider 40, and then the slider 40 at the dead point is driven by the cross groove structure 30 to continue to rotate, realizing the stable operation of the fluid machine. The dead point position of the motion mechanism is avoided, and the motion reliability of the fluid machinery is improved, thereby ensuring the working reliability of the heat exchange equipment.

It should be noted that, in this application, the maximum moment arm of the driving torque of the eccentric portion 11 is 2e.

Under this movement method, the running track of the slider 40 is a circle, and the circle takes the axis O ₀ of the crankshaft 10 as the center and the connecting line O ₀ O ₁ as the radius.

It should be noted that, in this application, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 times to complete 4 intake and exhaust processes.

Five optional implementations will be given below to introduce the structure of the fluid machine in detail, so as to better explain the operation method of the fluid machine through structural features.

Embodiment one

As shown in FIGS. 3 to 34 , in this embodiment, both ends of the intersecting groove structure 30 are provided with supporting convex rings 36 , and along the axial direction of the intersecting groove structure 30 , the inner ring of the supporting convex ring 36 faces the intersecting groove structure 30 The middle part of the crankshaft 10 passes through and forms a channel 39 , the channel 39 is concentrically arranged with the supporting convex ring 36 , and the channel 39 communicates with the limiting channel 31 .

As shown in Figures 3 to 34, the end cover 100 includes a flange 50 and a limiting plate 110, the flange 50 is arranged at the end of the cylinder liner 20, and the limiting plate 110 is arranged between the flange 50 and the cylinder liner 20, The limiting plate 110 has a through hole 1101 for avoiding the crankshaft 10, the height of the supporting convex ring 36 is greater than the thickness of the limiting plate 110, and the end face of the supporting convex ring 36 facing the flange 50 is used as the thrust surface 361, and the supporting convex ring 36 passes through the via hole 1101 and makes thrust contact with the flange 50 . In this way, only the thrust surface 361 of the support collar 36 is brought into thrust contact with the flange 50 .

In some embodiments, the height of the supporting convex ring 36 and the thickness of the limiting plate 110 meet: the height difference between the two ranges from 0.05 mm to 1 mm.

As shown in Figures 3 to 34, the end cover 100 includes a flange 50 and a limiting plate 110, the flange 50 is arranged at the end of the cylinder liner 20, and the limiting plate 110 is arranged between the flange 50 and the cylinder liner 20, The limiting plate 110 has a through hole 1101 for avoiding the crankshaft 10, and the supporting convex ring 36 is inserted into the through hole 1101. The height of the supporting convex ring 36 is smaller than the thickness of the limiting plate 110. The outer supporting ring surface 37 is in thrust contact with the limiting plate 110 . In this way, the end surface of the supporting convex ring 36 is suspended in the air, and at the same time, the supporting ring surface 37 outside the supporting convex ring 36 is in thrust contact with the limiting plate 110 .

It should be noted that, in this application, the limiting plate 110 is arranged concentrically with the intersecting groove structure 30 , and the through hole 1101 is a central hole of the limiting plate 110 .

As shown in Figures 3 to 26, the flange 50 is arranged at the axial end of the cylinder liner 20, the crankshaft 10 is concentrically arranged with the flange 50, the intersecting groove structure 30 is coaxially arranged with the cylinder liner 20, and the crankshaft 10 and the intersecting groove The assembly eccentricity of the structure 30 is determined by the relative positional relationship between the flange 50 and the cylinder liner 20, wherein the flange 50 is fixed on the cylinder liner 20 by a fastener 90, and the axis of the flange 50 and the axis of the inner ring of the cylinder liner 20 The relative position of the center is controlled by the alignment of the flange 50. The relative position of the axis of the flange 50 and the axis of the inner ring of the cylinder liner 20 determines the relative position of the axis of the crankshaft 10 and the axis of the cross groove structure 30. The essence of the alignment of the flange 50 is to make the eccentricity of the eccentric part 11 equal to the assembly eccentricity of the crankshaft 10 and the cylinder liner 20 .

Specifically, as shown in FIG. 12, the eccentricity of the two eccentric parts 11 is equal to e, and as shown in FIG. 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 liner 20), and the flange 50 includes an upper flange 52 and a lower flange 53, as shown in Figure 15 As shown, the distance between the axis of the inner ring of the cylinder liner 20 and the axis of the inner ring of the limiting plate 110 is e, which is equal to the eccentricity of the eccentric portion 11 .

In some embodiments, there is a first assembly gap between the crankshaft 10 and the flange 50, and the range of the first assembly gap is 0.005mm˜0.05mm.

In some embodiments, the range of the first assembly gap is 0.01-0.03 mm.

As shown in FIG. 5 , FIG. 6 , FIG. 8 and FIG. 10 , both ends of the limiting channel 31 penetrate to the outer peripheral surface of the intersecting groove structure 30 . In this way, it is beneficial to reduce the manufacturing difficulty of the intersecting groove structure 30 .

In some embodiments, the two sliders 40 are arranged concentrically with the two eccentric parts 11 respectively, the sliders 40 make a circular motion around the axis of the crankshaft 10, and there is a first rotation between the wall of the through hole 41 and the eccentric parts 11. The gap, the range of the first rotation gap is 0.005mm-0.05mm.

In some embodiments, the intersecting groove structure 30 is arranged coaxially with the cylinder liner 20, and there is a second rotation gap between the outer peripheral surface of the intersecting groove structure 30 and the inner wall surface of the cylinder liner 20, and the size of the second rotation gap is 0.005mm- 0.1mm.

As shown in FIG. 4 to FIG. 7 and FIG. 11 to FIG. 13 , the shaft body part 12 of the crankshaft 10 is integrally formed, and the shaft body part 12 has only one shaft center. In this way, the one-time molding of the shaft part 12 is facilitated, thereby reducing the difficulty of manufacturing the shaft part 12 .

It should be noted that, in an unillustrated embodiment of the present application, the shaft portion 12 of the crankshaft 10 includes a first section and a second section connected along its axial direction, the first section and the second section are arranged coaxially, Two eccentric portions 11 are respectively arranged on the first segment and the second segment.

In some embodiments, the first segment is detachably connected to the second segment. In this way, ease of assembly and disassembly of the crankshaft 10 is ensured.

As shown in FIGS. 4 to 7 and 11 to 13 , the shaft portion 12 of the crankshaft 10 and the eccentric portion 11 are integrally formed. In this way, one-shot forming of the crankshaft 10 is facilitated, thereby reducing the difficulty of manufacturing the crankshaft 10 .

It should be noted that, in an unillustrated embodiment of the present application, the shaft portion 12 of the crankshaft 10 is detachably connected to the eccentric portion 11 . In this way, the installation and removal of the eccentric portion 11 is facilitated.

It should be noted that, in the present application, the first included angle A is 160°-200°; the second included angle B is 80°-100°. In this way, it only needs to satisfy the relationship that the first included angle A is twice the second included angle B.

In some embodiments, the first included angle A is 160 degrees, and the second included angle B is 80 degrees.

In some embodiments, the first included angle A is 165 degrees, and the second included angle B is 82.5 degrees.

In some embodiments, the first included angle A is 170 degrees, and the second included angle B is 85 degrees.

In some embodiments, the first included angle A is 175 degrees, and the second included angle B is 87.5 degrees.

In some embodiments, the first included angle A is 180 degrees, and the second included angle B is 90 degrees.

In some embodiments, the first included angle A is 185 degrees, and the second included angle B is 92.5 degrees.

In some embodiments, the first included angle A is 190 degrees, and the second included angle B is 95 degrees.

In some embodiments, the first included angle A is 195 degrees, and the second included angle B is 97.5 degrees.

It should be noted that, in the present application, the eccentric portion 11 has an arc surface, and the central angle of the arc surface is greater than or equal to 180 degrees. In this way, it is ensured that the arc surface of the eccentric portion 11 can exert an effective driving force on the slider 40 , thereby ensuring the reliability of the movement of the slider 40 .

As shown in FIGS. 4 to 7 and 11 to 13 , the eccentric portion 11 is cylindrical.

In some embodiments, the proximal end of the eccentric portion 11 is flush with the outer circle of the shaft portion of the crankshaft 10 .

In some embodiments, the proximal end of the eccentric portion 11 protrudes beyond the outer circle of the shaft portion of the crankshaft 10 .

In some embodiments, the proximal end of the eccentric portion 11 is located inside the outer circle of the shaft portion of the crankshaft 10 .

It should be noted that, in an unillustrated embodiment of the present application, the slider 40 includes a plurality of substructures, and the plurality of substructures are spliced to form a through hole 41 .

As shown in FIG. 4 to FIG. 7 and FIG. 11 to FIG. 13 , two eccentric portions 11 are arranged at intervals in the axial direction of the crankshaft 10 . In this way, during the process of assembling the crankshaft 10 , the cylinder liner 20 and the two sliders 40 , ensuring the distance between the two eccentric parts 11 can provide an assembly space for the cylinder liner 20 to ensure the convenience of assembly.

As shown in FIG. 8 , the intersecting groove structure 30 has a central hole 32 through which the two limiting passages 31 communicate. The diameter of the central hole 32 is larger than the diameter of the shaft portion of the crankshaft 10 . In this way, it is ensured that the crankshaft 10 can pass through the central hole 32 smoothly.

In some embodiments, the diameter of the central hole 32 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 smoothly pass through the central hole 32 .

As shown in FIG. 16 , the axial projection of the slider 40 on 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 first sliding surfaces oppositely disposed in sliding contact with the slider 40 , the sliding block 40 has a second sliding surface cooperating with the first sliding surfaces, and the sliding block 40 has a The extrusion surface 42 at the end of the slider 40 is used as the head of the slider 40, and the two second sliding surfaces are connected by the extrusion surface 42, and the extrusion surface 42 faces the variable volume chamber 311. In this way, the projection of the second sliding surface of the slider 40 in the axial direction of the through hole 41 is a straight line segment, and at the same time, the projection of the extrusion surface 42 of the slider 40 in the axial direction of the through hole 41 is an arc segment.

Specifically, the extrusion 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 eccentricity of the eccentric portion 11 . In Fig. 16, the center of the through hole 41 of the slider 40 is the O _slider , and the distance between the arc centers of the two arc surfaces and the center of the through hole 41 is e, that is, the eccentricity of the eccentric portion 11, as shown in Fig. 16 The dotted line of X indicates the circle where the arc centers of the two arc surfaces are located.

In some embodiments, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner 20 .

In some embodiments, there is a difference between the radius of curvature of the arc surface and the radius of the inner circle of the cylinder liner 20, and the range of the difference is -0.05mm˜0.025mm.

In some embodiments, the difference ranges from -0.02 to 0.02 mm.

As shown in FIG. 8 , FIG. 9 , and FIG. 31 to FIG. 34 , the shape of the slider 40 on the section of the limiting channel 31 is adapted to the shape of the section of the limiting channel 31 . In this way, the sliding stability of the slider 40 in the limiting channel 31 is ensured.

As shown in Figure 31 to Figure 34, Figure 31 shows the chamfering of the direction slider and the corresponding intersecting groove structure 30, Figure 32 shows the trapezoidal slider and the corresponding intersecting groove structure 30, Figure 33 shows the chamfering of the trapezoidal slider and the corresponding The intersecting groove structure 30, FIG. 34 shows a semicircle+straight edge slider and the corresponding intersecting groove structure 30.

In some embodiments, the section of the limiting channel 31 is one of semicircle, circle, rectangle, ellipse, square and trapezoid.

In some embodiments, the projected area of the extrusion surface 42 in the sliding direction of the slider 40 is the S _slider , the exhaust area of the compression exhaust port 22 of the cylinder liner 20 is the S _row , and the value of the S _slider /S _row is 8 to 25.

In some embodiments, the value of S _slider /S _row is 12-18.

It should be noted that the fluid machine shown in this embodiment is a compressor. As shown in FIG. The lower cover assembly 85, wherein the liquid separator part 80 is arranged on the outside of the housing assembly 81, the upper cover assembly 84 is assembled on the upper end of the housing assembly 81, the lower cover assembly 85 is assembled on the lower end of the housing assembly 81, and the motor assembly 82 Both the motor assembly 82 and the pump body assembly 83 are located inside the housing assembly 81 , wherein 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 , the cylinder liner 20 , the intersecting groove structure 30 , the slider 40 , the upper flange 52 and the lower flange 53 .

In some embodiments, the above components are connected by means of welding, shrink fitting, or cold pressing.

The assembly process of the entire pump body assembly 83 is as follows: the lower flange 53 is fixed on the cylinder liner 20, the two sliders 40 are respectively placed in the corresponding two limiting passages 31, and the two eccentric parts 11 of the crankshaft 10 respectively extend into the In the two through holes 41 of the corresponding two sliders 40, the assembled crankshaft 10, the cross groove structure 30 and the two sliders 40 are placed in the cylinder liner 20, and one end of the crankshaft 10 is installed on the lower flange 53 , the other end of the crankshaft 10 is set through the upper flange 52 , see FIG. 4 and FIG. 5 for details.

It should be noted that, in this embodiment, the closed space surrounded by the slider 40, the limiting channel 31, the cylinder liner 20 and the upper flange 52 (or the lower flange 53) is the variable volume chamber 311, and the pump body assembly 83 has four variable volume chambers 311 in total. During the rotation of the crankshaft 10, the crankshaft 10 rotates 2 revolutions, and a single variable volume chamber 311 completes one intake and exhaust process. For the compressor, the crankshaft 10 rotates 2 revolutions, totaling Complete 4 suction and exhaust processes.

As shown in Figures 25 to 30, the sliding block 40 rotates relative to the cylinder liner 20 during the reciprocating movement in the limiting channel 31. In Figures 25 to 27, the sliding block 40 is clockwise from 0° to 180° During the rotation process, the variable volume chamber 311 increases. During the process of increasing the variable volume chamber 311, the variable volume chamber 311 communicates with the suction chamber 23 of the cylinder liner 20. When the slider 40 rotates to 180 degrees, the variable volume chamber The volume of 311 reaches the maximum value, and at this time, the variable volume chamber 311 is separated from the suction chamber 23, thus completing the suction operation. In Figures 28 to 30, the slider 40 continues to rotate clockwise from 180 degrees to 360 degrees During the process, the variable volume chamber 311 decreases, and the slider 40 compresses the gas in the variable volume chamber 311. When the slider 40 rotates until the variable volume chamber 311 communicates with the compression exhaust port 22, and when the variable volume chamber 311 When the gas inside reaches the exhaust pressure, the exhaust valve plate 61 of the exhaust valve assembly 60 opens, and the exhaust operation starts until the compression ends and enters the next cycle.

As shown in Figures 25 to 30, the point marked with M is used as the reference point for the relative movement of the slider 40 and the crankshaft 10, and Figure 26 shows the process of the slider 40 rotating clockwise from 0° to 180°, the rotation of the slider 40 The angle is θ1, and the corresponding rotation angle of the crankshaft 10 is 2θ1. Fig. 28 shows that the slider 40 continues to rotate clockwise from 180° to 360°, and the rotation angle of the slider 40 is 180°+θ2. The crankshaft 10 rotates at an angle of 360°+2θ2. Figure 29 shows that the slider 40 continues to rotate clockwise from 180° to 360°, and the variable volume cavity 311 communicates with the compression exhaust port 22, and the slider 40 rotates The angle is 180°+θ3, and the corresponding rotation angle of the crankshaft 10 is 360°+2θ3, that is, the slider 40 rotates once, and the corresponding crankshaft 10 rotates twice, wherein, θ1<θ2<θ3.

Specifically, as shown in FIGS. 17 to 30 , the cylinder liner 20 has a compression intake port 21 and a compression exhaust port 22 . When any slider 40 is at the intake position, the compression intake port 21 and the corresponding variable The volume cavity 311 is in communication; when any slider 40 is in the exhaust position, the corresponding variable volume cavity 311 is in communication with the compression exhaust port 22 .

As shown in FIG. 17 to FIG. 20 and FIG. 24 to FIG. 30 , the inner wall surface of the cylinder liner 20 has an air suction chamber 23 , and the air suction chamber 23 communicates with the compressed air inlet 21 . In this way, it is ensured that the suction chamber 23 can store a large amount of gas, so that the variable volume chamber 311 can be fully suctioned, so that the compressor can take in enough air, and when the suction is insufficient, the stored gas can be supplied in time Give the variable volume chamber 311 to ensure the compression efficiency of the compressor.

In some embodiments, the suction cavity 23 is a cavity formed by radially hollowing out the inner wall of the cylinder liner 20 , and there may be one suction cavity 23 or two upper and lower ones.

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

As shown in Figure 17 and Figure 19, there are two suction cavities 23, and the two suction cavities 23 are arranged at intervals along the axial direction of the cylinder liner 20. The cylinder liner 20 also has a suction communication cavity 24, and the two suction cavities 23 Both communicate with the suction communication chamber 24 , and the compressed air inlet 21 communicates with the suction chamber 23 through the suction communication chamber 24 . In this way, it is beneficial to increase the volume of the suction cavity 23, thereby reducing the suction pressure pulsation.

Specifically, the suction communication cavity 24 extends a second preset distance along the axial direction of the cylinder liner 20 , and at least one end of the suction communication cavity 24 passes through the axial end surface of the cylinder liner 20 . In this way, it is convenient to open the suction communication cavity 24 from the end surface of the cylinder liner 20 , ensuring the convenience of processing the suction communication cavity 24 .

As shown in Figures 17 to 30, an exhaust cavity 25 is opened on the outer wall of the cylinder liner 20, and the compression exhaust port 22 is connected to the exhaust cavity 25 by the inner wall of the cylinder liner 20, and the fluid machine also includes an exhaust valve assembly 60 , the exhaust valve assembly 60 is disposed in the exhaust chamber 25 and is disposed corresponding to the compression exhaust port 22 . In this way, the exhaust cavity 25 is used to accommodate the exhaust valve assembly 60 , which effectively reduces the occupied space of the exhaust valve assembly 60 , makes the components reasonably arranged, and improves the space utilization rate of the cylinder liner 20 .

As shown in Figure 19, Figure 21 to Figure 23, there are two compression exhaust ports 22, and the two compression exhaust ports 22 are arranged at intervals along the axial direction of the cylinder liner 20. The gas valve assembly 60 is respectively provided corresponding to the two compression and exhaust ports 22 . In this way, since the two compression exhaust ports 22 are respectively provided with two sets of exhaust valve assemblies 60, a large amount of gas leakage in the variable volume chamber 311 is effectively avoided, and the compression efficiency of the variable volume chamber 311 is ensured.

As shown in Figure 20, the exhaust valve assembly 60 is connected to the cylinder liner 20 through a fastener 90, the exhaust valve assembly 60 includes an exhaust valve plate 61 and a valve plate baffle 62, and the exhaust valve plate 61 is arranged in the exhaust cavity 25 and cover the corresponding compression exhaust port 22, the valve plate baffle 62 is overlapped on the exhaust valve plate 61. In this way, the setting of the valve plate baffle 62 effectively prevents the excessive opening of the exhaust valve plate 61 , thereby ensuring the exhaust performance of the cylinder liner 20 .

In some embodiments, fasteners 90 are screws.

As shown in Fig. 17, Fig. 22 and Fig. 23, a communication hole 26 is also provided on the axial end surface of the cylinder liner 20, and the communication hole 26 communicates with the exhaust chamber 25, and the end cover 100 includes a flange 50 and a limit plate 110, The flange 50 is arranged at the end of the cylinder liner 20, the limiting plate 110 is arranged between the flange 50 and the cylinder liner 20, the flange 50 is provided with an exhaust channel 51, the limiting plate 110 is opposite to the exhaust channel 51 An avoidance channel 1102 is provided at the position, and the communication hole 26 communicates with the exhaust channel 51 through the avoidance channel 1102 . In this way, the exhaust reliability of the cylinder liner 20 is ensured.

As shown in FIG. 24 , the exhaust cavity 25 penetrates to the outer wall of the cylinder liner 20 , and the fluid machine further includes an exhaust cover 70 , which is connected to the cylinder liner 20 and seals the exhaust cavity 25 . In this way, the exhaust cover plate 70 plays a role of isolating the variable volume chamber 311 from the external space of the pump body assembly 83 .

As shown in Figure 22 and Figure 23, when the variable volume chamber 311 communicates with the compression exhaust port 22, when the pressure of the variable volume chamber 311 reaches the exhaust pressure, the exhaust valve plate 61 opens, and the compressed gas passes through the compression exhaust port 22 enters the exhaust cavity 25, and passes through the communication hole 26 on the cylinder liner 20, then is discharged through the exhaust passage 51 and enters the external space of the pump body assembly 83 (that is, the cavity of the compressor), thereby completing the exhaust process .

In some embodiments, exhaust cover plate 70 is secured to cylinder liner 20 by fasteners 90 .

In some embodiments, fasteners 90 are screws.

In some embodiments, the outer contour of the exhaust cover 70 matches the outer contour of the exhaust cavity 25 .

The following is a detailed introduction to the operation of the compressor:

As shown in Figure 3, the motor assembly 82 drives the crankshaft 10 to rotate, and the two eccentric parts 11 of the crankshaft 10 respectively drive the corresponding two sliders 40 to move. When the slider 40 revolves around the axis of the crankshaft 10, the slider 40 Relative to the eccentric part 11, the slider 40 reciprocates along the limiting channel 31, and drives the cross groove structure 30 to rotate in the cylinder liner 20. The slider 40 reciprocates along the limiting channel 31 while revolving to form a cross slide Movement mode of the block mechanism.

Other usage occasions: the compressor can be used as an expander by exchanging the positions of the suction port and the exhaust port. That is, the exhaust port of the compressor is used as the suction port of the expander, and high-pressure gas is passed in, and other pushing mechanisms rotate, and the gas is discharged through the suction port of the compressor (exhaust port of the expander) after expansion.

When the fluid machine is an expander, the cylinder liner 20 has an expansion exhaust port and an expansion intake port. When any slider 40 is in the intake position, the expansion exhaust port is in communication with the corresponding variable volume chamber 311; When a slider 40 is in the exhaust position, the corresponding variable volume cavity 311 is in communication with the expansion inlet.

In some embodiments, the inner wall of the cylinder liner 20 has an expansion exhaust cavity, and the expansion exhaust cavity communicates with the expansion exhaust port.

Further, the expansion exhaust chamber extends a first preset distance around the circumference of the inner wall surface of the cylinder liner 20 to form an arc-shaped expansion exhaust chamber, and the expansion exhaust chamber extends from the expansion exhaust port to the expansion intake port. One side extends, and the extension direction of the expansion and exhaust chamber is the same as the rotation direction of the intersecting groove structure 30 .

Further, there are two expansion and exhaust cavities, and the two expansion and exhaust cavities are arranged at intervals along the axial direction of the cylinder liner 20. The cylinder liner 20 also has an expansion and exhaust communication cavity, and both expansion and exhaust cavities communicate with the expansion and exhaust The cavity is communicated, and the expansion exhaust port is communicated with the expansion exhaust cavity through the expansion exhaust communication cavity.

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

Embodiment two

As shown in Figures 35 to 53, only one end of the intersecting groove structure 30 has a supporting protruding ring 36, and the end face of the end of the intersecting groove structure 30 not provided with a supporting protruding ring 36 is open, and the limiting channel 31 is arranged along the intersecting groove structure. The axial direction of 30 directly penetrates to the end face.

In this embodiment, one end with an open end face is located below the intersecting groove structure 30 .

The air intake and exhaust method of this embodiment is the same as that of the first embodiment, and will not be repeated here.

As shown in FIGS. 40 and 41 , in this embodiment, the cross sections of the two sliders 40 are determined according to the two limiting channels 31 of the intersecting groove structure 30 .

As shown in FIG. 48 and FIG. 49 , bearings 200 are sheathed on both axial ends of the intersecting groove structure 30 .

As shown in FIG. 50 , the axial end of the intersecting groove structure 30 is sleeved with a bearing 200 , and is located above the axial end of the intersecting groove structure 30 .

As shown in FIG. 51 , the other axial end of the intersecting groove structure 30 is sleeved with a bearing 200 , and is located below one axial end of the intersecting groove structure 30 .

As shown in Figure 52 and Figure 53, the bearing 200 is arranged in the cylinder liner 20 and the outer ring of the bearing 200 is attached to the inner wall of the cylinder liner 20, and the ratio between the height H1 of the bearing 200 and the height H2 of the cylinder liner 20 is defined at the same time Greater than 0.9 and less than 1.

Embodiment Three

As shown in Figures 54 to 56, only one end of the intersecting groove structure 30 has a supporting convex ring 36, and the end surface of the end of the intersecting groove structure 30 not provided with a supporting convex ring 36 is open, and the limiting channel 31 is along the cross groove structure. The axial direction of 30 directly penetrates to the end surface.

In this embodiment, one end with an open end face is located above the intersecting groove structure 30 .

Embodiment Four

As shown in Figures 57 to 59, only one end of the intersecting groove structure 30 has a supporting protruding ring 36, and the end surface of the end of the intersecting groove structure 30 that is not provided with a supporting protruding ring 36 is only reserved with an opening 38 for the crankshaft 10 to protrude from. , the opening 38 is set concentrically with the supporting convex ring 36 , and the opening 38 communicates with the limiting channel 31 .

In this embodiment, the end surface of the lower end of the intersecting groove structure 30 only reserves an opening 38 for the crankshaft 10 to protrude from.

Embodiment five

As shown in FIGS. 60 to 62 , only the opening 38 for the crankshaft 10 is reserved on the end surface of the upper end of the intersecting groove structure 30 .

It should be noted that the terminology used here is only for describing specific implementations, and is not intended to limit the exemplary implementations according to the present application. As used herein, unless the context clearly dictates otherwise, the singular is intended to include the plural, and it should also be understood that when the terms "comprising" and/or "comprising" are used in this specification, they mean There are features, steps, operations, means, components and/or combinations thereof.

Relative arrangements of components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present disclosure unless specifically stated otherwise. At the same time, it should be understood that, for the convenience of description, the sizes of the various parts shown in the drawings are not drawn according to the actual proportional relationship. Techniques, methods and devices known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, such techniques, methods and devices should be considered part of the Authorized Specification. In all examples shown and discussed herein, any specific values should be construed as illustrative only, and not as limiting. Therefore, other examples of the exemplary embodiment may have different values. It should be noted that like numbers and letters denote similar items in the following figures, therefore, once an item is defined in one figure, it does not require further discussion in subsequent figures.

For the convenience of description, spatially relative terms may be used here, such as "on ...", "over ...", "on the surface of ...", "above", etc., to describe The spatial positional relationship between one device or feature shown and other devices or features. It will be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, devices described as "above" or "above" other devices or configurations would then be oriented "beneath" or "above" the other devices or configurations. under other devices or configurations”. Thus, the exemplary term "above" can encompass both an orientation of "above" and "beneath". The device may be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptions used herein interpreted accordingly.

It should be noted that the terms "first" and "second" in the description and claims of the present application and the above drawings are used to distinguish similar objects, but not necessarily used to describe a specific sequence or sequence. It is to be understood that the data so used are interchangeable under appropriate circumstances such that the embodiments of the application described herein can be practiced in sequences other than those illustrated or described herein.

The above descriptions are only optional embodiments of the present disclosure, and are not intended to limit the present disclosure. For those skilled in the art, the present disclosure may have various modifications and changes. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present disclosure shall be included within the protection scope of the present disclosure.

Claims

A fluid machine comprising:

A crankshaft (10), the crankshaft (10) is provided with two eccentric parts (11) along its axial direction, and there is a phase difference of a first angle A between the two eccentric parts (11);

A cylinder liner (20), the crankshaft (10) and the cylinder liner (20) are arranged eccentrically and the eccentric distance is fixed;

at least one end cover (100), the crankshaft (10) is disposed through the end cover (100) and the cylinder liner (20);

A cross groove structure (30), the cross groove structure (30) is rotatably arranged in the cylinder liner (20), the cross groove structure (30) has two limiting passages (31), and the two The 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 the two limiting channels There is a phase difference of a second included angle B between the extending directions of the bit channels (31), wherein the first included angle A is twice the second included angle B, and the intersecting slot structure (30) There is at least one supporting convex ring (36) in the axial direction, and the outer diameter of the supporting convex ring (36) is smaller than the outer diameter of the cross groove structure (30), and the supporting convex ring (36) faces the The end cover (100) stretches out;

Slide block (40), described slide block (40) has through hole (41), and described slide block (40) is two, and two described eccentric parts (11) extend into two described slide blocks ( 40) in the two through holes (41), the two sliders (40) are correspondingly slidably arranged in the two limiting passages (31) and form variable volume chambers (311), the variable volume The volume cavity (311) is located in the sliding direction of the slider (40), and the crankshaft (10) rotates to drive the slider (40) to slide back and forth in the limiting channel (31) while intersecting with the The groove structure (30) interacts so that the intersecting groove structure (30) and the slider (40) rotate in the cylinder sleeve (20).
The fluid machine according to claim 1, wherein the end cover (100) comprises:

A flange (50) and a limiting plate (110), the flange (50) is arranged on the end of the cylinder liner (20), and the limiting plate (110) is arranged on the flange (50) Between the cylinder liner (20), the limiting plate (110) has a through hole (1101) for avoiding the crankshaft (10), and the height of the supporting convex ring (36) is greater than the limiting plate (110). The thickness of the bit plate (110), the end face of the supporting convex ring (36) facing the flange (50) side is used as the thrust surface (361), and the supporting convex ring (36) passes through the through hole (1101) and thrust contact with said flange (50).
The fluid machine according to claim 2, wherein the height of the supporting convex ring (36) and the thickness of the limiting plate (110) meet: the height difference between the two ranges from 0.05 mm to 1 mm.
The fluid machine according to claim 1, wherein the end cover (100) comprises:

A flange (50) and a limiting plate (110), the flange (50) is arranged on the end of the cylinder liner (20), and the limiting plate (110) is arranged on the flange (50) Between the cylinder liner (20), the limiting plate (110) has a through hole (1101) for avoiding the crankshaft (10), and the supporting convex ring (36) extends into the through hole (1101), the height of the supporting convex ring (36) is smaller than the thickness of the limiting plate (110), and the intersecting groove structure (30) is located on the supporting ring surface outside the supporting convex ring (36). (37) is in thrust contact with the limiting plate (110).
The fluid machine according to claim 4, wherein the height difference between the height of the supporting convex ring (36) and the thickness of the limiting plate (110) ranges from 0.05 mm to 1 mm.
The fluid machine according to one of claims 2 and 3 or one of claims 4 and 5, wherein the limiting plate (110) is arranged concentrically with the intersecting groove structure (30), and the through hole (1101) is the central hole of the limiting plate (110).
The fluid machine according to any one of claims 1-6, wherein only one end of the intersecting groove structure (30) has the supporting convex ring (36), wherein,

The end surface of the end of the intersecting groove structure (30) that is not provided with the supporting convex ring (36) is only reserved with an opening (38) for the crankshaft (10) to protrude from, and the opening (38) ) is arranged concentrically with the supporting convex ring (36), and the opening (38) communicates with the limiting channel (31); or,

The end surface of one end of the intersecting groove structure (30) that is not provided with the supporting convex ring (36) is open, and the limiting channel (31) is directly along the axial direction of the intersecting groove structure (30). through to the end face.
The fluid machine according to any one of claims 1-7, wherein both ends of the intersecting groove structure (30) have the supporting convex ring (36), along the axis of the intersecting groove structure (30) In the direction, the inner ring of the supporting convex ring (36) faces the middle part of the intersecting groove structure (30) and penetrates to form a channel (39) for the crankshaft (10) to pass through, and the channel (39) is connected with the The supporting convex ring (36) is arranged concentrically, and the channel (39) communicates with the limiting channel (31).
The fluid machine according to one of claims 2 and 3 or one of claims 4 and 5, wherein said crankshaft (10) is arranged concentrically with said flange (50).
The fluid machine according to claim 9, wherein there is a first assembly gap between the crankshaft (10) and the flange (50), and the range of the first assembly gap is 0.005mm-0.05mm.
The fluid machine according to claim 10, wherein the first assembly clearance ranges from 0.01 to 0.03 mm.
The fluid machine according to any one of claims 1 to 11, wherein the eccentricity of the eccentric part (11) is equal to the assembly eccentricity of the crankshaft (10) and the cylinder liner (20).
The fluid machine according to any one of claims 1 to 12, wherein both ends of the limiting channel (31) penetrate to the outer peripheral surface of the intersecting groove structure (30).
The fluid machine according to any one of claims 1 to 13, wherein the two sliders (40) are arranged concentrically with the two eccentric parts (11) respectively, and the sliders (40) surround the The axis of the crankshaft (10) makes a circular motion, and there is a first rotation gap between the wall of the through hole (41) and the eccentric part (11), and the range of the first rotation gap is 0.005 mm to 0.05 mm. mm.
The fluid machine according to any one of claims 1 to 14, wherein the intersecting groove structure (30) is arranged coaxially with the cylinder liner (20), and the outer peripheral surface of the intersecting groove structure (30) and the There is a second rotation gap between the inner wall surfaces of the cylinder liner (20), and the range of the second rotation gap is 0.005mm-0.1mm.
The fluid machine according to any one of claims 1 to 15, wherein the first included angle A ranges from 160° to 200°; the second included angle B ranges from 80° to 100°.
The fluid machine according to any one of claims 1 to 16, wherein the eccentric portion (11) has an arc surface, and the central angle of the arc surface is greater than or equal to 180 degrees.
The fluid machine according to any one of claims 1 to 17, wherein the eccentric portion (11) is cylindrical.
The fluid machine according to claim 18, wherein the proximal end of the eccentric portion (11) is arranged as one of the following:

The proximal end of the eccentric part (11) is flush with the outer circle of the shaft part of the crankshaft (10);

The proximal end of the eccentric part (11) protrudes from the outer circle of the shaft part of the crankshaft (10);

The proximal end of the eccentric portion (11) is located inside the outer circle of the shaft portion of the crankshaft (10).
The fluid machine according to any one of claims 1 to 19, wherein the two eccentric portions (11) are arranged at intervals in the axial direction of the crankshaft (10).
The fluid machine according to any one of claims 1 to 20, wherein the intersecting groove structure (30) has a central hole (32), and the two limiting passages (31) pass through the central hole (32) In communication, the diameter of the central hole (32) is greater than the diameter of the shaft portion of the crankshaft (10).
The fluid machine according to claim 21, wherein the diameter of the central hole (32) is larger than the diameter of the eccentric portion (11).
The fluid machine according to any one of claims 1 to 22, wherein the limiting channel (31) has a set of oppositely disposed first sliding surfaces in sliding contact with the slider (40), the The slider (40) has a second sliding surface matched with the first sliding surface, the slider (40) has a pressing surface (42) facing the end of the limiting channel (31), The extrusion surface (42) serves as the head of the slider (40), the two second sliding surfaces are connected through the extrusion surface (42), and the extrusion surface (42) faces the Describe variable volume cavity (311).
The fluid machine according to claim 23, wherein the extrusion 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 portion ( 11) The amount of eccentricity.
The fluid machine according to claim 24, wherein,

The radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner (20); or,

There is a difference between the radius of curvature of the arc surface and the radius of the inner circle of the cylinder liner (20), and the range of the difference is -0.05mm˜0.025mm.
The fluid machine according to claim 25, wherein said difference ranges from -0.02 to 0.02 mm.
The fluid machine according to any one of claims 1 to 26, wherein the shape of the slider (40) on the section of the limiting channel (31) is the same as that of the section of the limiting channel (31) The shape matches.
The fluid machine according to any one of claims 23 to 27, wherein the cylinder liner (20) has a compression intake port (21) and a compression discharge port (22),

When any one of the sliders (40) is at the air intake position, the compression air inlet (21) is connected to the corresponding variable volume chamber (311);

When any one of the sliders (40) is in the exhaust position, the corresponding variable volume cavity (311) is in communication with the compression exhaust port (22).
The fluid machine according to claim 28, wherein the projected area of the extrusion surface (42) in the sliding direction of the slider (40) is S slider , and the compression exhaust port of the cylinder liner (20) The exhaust area of (22) is S row , and the range of ratio S slide block /S row is 8～25.
The fluid machine according to claim 29, wherein the ratio S slider /S row ranges from 12 to 18.
The fluid machine according to any one of claims 28 to 30, wherein the inner wall of the cylinder liner (20) has an air suction chamber (23), and the air suction chamber (23) is connected to the compressed air inlet (21) CONNECTED.
The fluid machine according to claim 31, wherein the suction cavity (23) extends a first preset distance around the inner wall surface of the cylinder liner (20) to form an arc-shaped suction cavity (23) .
The fluid machine according to claim 31 or 32, wherein two said suction cavities (23) are arranged at intervals along the axial direction of said cylinder liner (20), and said cylinder liner (20) also has a suction communication cavity (24), both of the suction chambers (23) communicate with the suction communication chamber (24), and the compressed air inlet (21) communicates with the suction communication chamber (24) The suction cavity (23) is connected.
The fluid machine according to claim 33, wherein the suction communication cavity (24) extends a second preset distance along the axial direction of the cylinder liner (20), and at least one end of the suction communication cavity (24) Through the axial end surface of the cylinder liner (20).
The fluid machine according to any one of claims 28 to 34, wherein an exhaust chamber (25) is opened on the outer wall of the cylinder liner (20), and the compression exhaust port (22) is controlled by the cylinder liner The inner wall of (20) communicates with the exhaust cavity (25), the fluid machine also includes an exhaust valve assembly (60), and the exhaust valve assembly (60) is arranged in the exhaust cavity (25) Inside and set corresponding to the compression exhaust port (22).
The fluid machine according to claim 35, wherein the two compression exhaust ports (22) are arranged at intervals along the axial direction of the cylinder liner (20), and the exhaust valve assemblies (60) are in two groups, two A set of exhaust valve assemblies (60) is set corresponding to the two compression exhaust ports (22).
The fluid machine according to claim 36, wherein a communication hole (26) is further provided on the axial end surface of the cylinder liner (20), and the communication hole (26) communicates with the exhaust chamber (25), The end cover (100) includes a flange (50) and a limiting plate (110), the flange (50) is arranged at the end of the cylinder liner (20), and the limiting plate (110) is arranged Between the flange (50) and the cylinder liner (20), an exhaust channel (51) is provided on the flange (50), and the limiting plate (110) and the exhaust channel An escape channel (1102) is provided at a position opposite to (51), and the communication hole (26) communicates with the exhaust channel (51) through the avoidance channel (1102).
The fluid machine according to any one of claims 35 to 37, wherein the exhaust cavity (25) penetrates to the outer wall surface of the cylinder liner (20), and the fluid machine further includes an exhaust cover plate (70 ), the exhaust cover plate (70) is connected with the cylinder liner (20) and seals the exhaust chamber (25).
The fluid machine according to any one of claims 28 to 38, wherein the fluid machine is a compressor.
The fluid machine according to any one of claims 1 to 27, wherein the cylinder liner (20) has an expansion exhaust port and an expansion intake port,

When any of the sliders (40) is at the intake position, the expansion exhaust port is connected to the corresponding variable volume cavity (311);

When any one of the sliders (40) is in the exhaust position, the corresponding variable volume chamber (311) communicates with the expansion inlet.
The fluid machine according to claim 40, wherein the inner wall of the cylinder liner (20) has an expansion exhaust cavity, and the expansion exhaust cavity communicates with the expansion exhaust port.
The fluid machine according to claim 41, wherein the expansion exhaust cavity extends a first preset distance around the inner wall surface of the cylinder liner (20) to form an arc-shaped expansion exhaust cavity, and the The expansion exhaust cavity extends from the expansion exhaust port to the side where the expansion intake port is located, and the extension direction of the expansion exhaust cavity is in the same direction as the rotation direction of the intersecting groove structure (30).
The fluid machine according to claim 42, wherein two expansion exhaust chambers are arranged at intervals along the axial direction of the cylinder liner (20), and the cylinder liner (20) also has an expansion exhaust communication cavity, two The inflation and exhaust chambers are all in communication with the inflation and exhaust communication chambers, and the expansion and exhaust ports are in communication with the inflation and exhaust chambers through the inflation and exhaust communication chambers.
The fluid machine according to claim 43, wherein the expansion exhaust communication cavity extends a second preset distance in the axial direction of the cylinder liner (20), and at least one end of the expansion exhaust communication cavity passes through the cylinder The axial end face of the sleeve (20).
A fluid machine according to any one of claims 40 to 44, wherein the fluid machine is an expander.
A heat exchange device, comprising the fluid machine according to any one of claims 1-45.