Fluid machinery and heat exchange equipment

Abstract

This invention provides a fluid machine and a heat exchange device. The fluid machine includes a crankshaft, a cylinder liner, a cross-groove structure, a slider, and two flanges. The crankshaft has two eccentric portions along its axial direction. The crankshaft and cylinder liner are eccentrically positioned with a fixed eccentricity. The cross-groove structure is rotatably disposed within the cylinder liner, and two limiting channels of the cross-groove structure are sequentially arranged along the axial direction of the crankshaft. The two eccentric portions extend into two through holes of the two sliders, and the two sliders are slidably disposed within the two limiting channels, forming a variable volume cavity located in the sliding direction of the sliders. Both flanges have exhaust channels, which communicate with the corresponding variable volume cavities. The cross-sectional area of ​​the exhaust channel is 0.5%-35% of the projected area of ​​the slider in its sliding direction. This invention solves the problems of low energy efficiency and high noise in existing compressors, as well as the difficulties in processing exhaust ports, reducing clearance volume, and minimizing noise.

Description

Technical Field

[0001] This invention relates to the field of heat exchange system technology, and more specifically, to a fluid machine and a heat exchange device. Background Technology

[0002] Fluid machinery in the prior art includes compressors and expanders, among others. Let's take compressors as an example.

[0003] In accordance with national energy conservation and environmental protection policies and consumer demands for air conditioning comfort, the air conditioning industry has been pursuing high efficiency and low noise. The compressor, as the heart of the air conditioner, directly impacts its energy efficiency and noise level. While the rolling rotor compressor, the mainstream type for household air conditioners, has matured after nearly a century of development, its structural design limits its potential for further optimization. Therefore, there is an urgent need to develop a compressor with high energy efficiency and low noise.

[0004] In addition, most existing compressors exhaust air through the side wall of the cylinder liner. In terms of parts processing, it is difficult to open exhaust ports on the curved surface, and the clearance volume caused by side exhaust is large, which also generates a lot of noise. Summary of the Invention

[0005] The main objective of this invention is to provide a fluid machinery and heat exchange device to solve the problems of low energy efficiency and high noise in existing compressors, as well as how to reduce the processing difficulty of the exhaust port, reduce clearance volume and noise.

[0006] To achieve the above objectives, according to one aspect of the present invention, a fluid machine is provided, comprising a crankshaft, a cylinder liner, a cross-groove structure, a slider, and two flanges. The crankshaft has two eccentric portions arranged along its axial direction; the crankshaft and cylinder liner are eccentrically arranged with a fixed eccentric distance; the cross-groove structure is rotatably disposed within the cylinder liner, and the cross-groove structure has two limiting channels, which are sequentially arranged along the axial direction of the crankshaft, with the extending direction of the limiting channels perpendicular to the axial direction of the crankshaft; the slider has through holes, and there are two sliders, with the two eccentric portions correspondingly extending into the two through holes of the two sliders. The two sliders are correspondingly slidably disposed within the two limiting channels and form a variable volume cavity, the variable volume cavity being located in the sliding direction of the slider. The crankshaft rotates to drive the sliders to reciprocate within the limiting channels while interacting with the cross-groove structure, causing the cross-groove structure and the sliders to rotate within the cylinder liner; the two flanges are respectively disposed at both axial ends of the cylinder liner, and each flange has an exhaust channel, which communicates with the variable volume cavity on the corresponding side; wherein the cross-sectional area of ​​the exhaust channel is 0.5%-35% of the projected area of ​​the slider in its sliding direction.

[0007] Furthermore, the projection of the slider in its sliding direction is a semicircle.

[0008] Furthermore, the axial projection of the slider in the through hole has two relatively parallel straight line segments and an arc segment connecting the ends of the two straight line segments; the exhaust passage is positioned in the circumferential direction of the flange within the angular range of (90°-arccos(C / D)~90°+arccos(C / D)), where C is the distance between the two relatively parallel straight line segments of the axial projection of the slider in the through hole, and D is the inner diameter of the cylinder liner.

[0009] Furthermore, oblique cuts are provided at the inner edges of both ends of the cylinder liner along the axial direction, and the two oblique cuts are used to connect with the two exhaust passages respectively.

[0010] Furthermore, the two exhaust passages are concentrically arranged in the axial direction of the cylinder liner, and the two oblique cuts are in the same position in the circumferential direction of the cylinder liner; or, the two exhaust passages are not concentrically arranged in the axial direction of the cylinder liner, and the two oblique cuts are in different positions in the circumferential direction of the cylinder liner.

[0011] Furthermore, the sum of the projected area of ​​the oblique cut on the inner circle of the cylinder liner and the projected area of ​​the oblique cut on the end face of the cylinder liner is greater than or equal to the cross-sectional area of ​​the exhaust passage.

[0012] Furthermore, a drainage groove is provided on the end face of the flange facing the cylinder liner. The drainage groove is connected to the exhaust channel and is positioned opposite to and connected to the oblique cut.

[0013] Furthermore, the cylinder liner has at least one radial intake port for communicating with the variable volume chamber, and the inner wall surface of the cylinder liner has an intake chamber, through which the radial intake port communicates with the variable volume chamber.

[0014] Furthermore, the intake chamber extends circumferentially around the inner wall of the cylinder liner by a first predetermined distance to form an arc-shaped intake chamber.

[0015] Furthermore, there are two intake chambers, which are spaced apart along the axial direction of the cylinder liner. The cylinder liner also has an intake communication chamber, and both intake chambers are connected to the intake communication chamber. When the cylinder liner has a radial intake hole, the radial intake hole is connected to the two intake chambers through the intake communication chamber.

[0016] Furthermore, the intake communication cavity extends a second predetermined distance along the axial direction of the cylinder liner, and at least one end of the intake communication cavity penetrates the axial end face of the cylinder liner.

[0017] Furthermore, there are two intake chambers, which are spaced apart along the axial direction of the cylinder liner. There are also two radial intake holes, which correspond one-to-one with the two intake chambers. The two radial intake holes are connected to the corresponding variable volume chambers through the two intake chambers respectively.

[0018] Furthermore, one of the two flanges has an intake passage, and the intake passage and the exhaust passage on the same flange have a phase difference in the circumferential direction of the flange. The cylinder liner has a radial intake port, and the intake passage and the radial intake port are respectively connected to two variable volume chambers.

[0019] Furthermore, both flanges have intake channels, and the intake and exhaust channels on the same flange have a phase difference in the circumferential direction of the flange. The two intake channels are respectively connected to two variable volume chambers.

[0020] Furthermore, there is a phase difference of a first included angle A between the two eccentric parts, the eccentricity of the two eccentric parts is equal, and there is a phase difference of a second included angle B between the extension directions of the two limiting channels, wherein the first included angle A is twice the second included angle B.

[0021] According to another aspect of the present invention, a heat exchange device is provided, including fluid machinery, wherein the fluid machinery is the fluid machinery described above.

[0022] By applying the technical solution of this invention, exhaust channels are opened on both flanges, and the two exhaust channels are respectively connected to the variable volume cavity on the corresponding side. In this way, since the exhaust channels are opened on the plane of the flange, compared with the existing ones opened on the side wall arc surface of the cylinder liner, it is beneficial to reduce the noise caused by the existence of sharp corners in the exhaust channels and the misalignment of the cylinder liner and flange during assembly. The exhaust path of the fluid machinery is changed to avoid the generation of noise. In addition, since the exhaust channels are opened on the plane of the flange and are on the outer plane, compared with those opened on the side wall arc surface of the cylinder liner, the processing difficulty of the exhaust channels is greatly reduced, the parts are easier to process, and it is beneficial to grind the burrs or edges caused by processing.

[0023] Furthermore, since both ends of the exhaust channel of the fluid machinery provided in this application are planes in the length direction, under the condition that the load-bearing thickness and the diameter of the exhaust channel are the same, the volume of the planar exhaust channel of this application is smaller and the clearance volume is also smaller, which is beneficial to ensuring the cooling capacity and reducing power consumption.

[0024] In addition, exhaust loss can be avoided by reasonably optimizing the cross-sectional area of ​​the exhaust channel and the proportion of the projected area of ​​the slider in its sliding direction. Attached Figure Description

[0025] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0026] Figure 1 A schematic diagram of the internal structure of a compressor according to an optional embodiment of the present invention is shown;

[0027] Figure 2 It shows Figure 1 A first-view cross-sectional structural schematic diagram of the pump body assembly of the compressor in the image;

[0028] Figure 3 It shows Figure 2 An exploded view of the pump body components;

[0029] Figure 4 It shows Figure 3 A schematic diagram of the assembly structure of the crankshaft, cross groove structure, and slider;

[0030] Figure 5 It shows Figure 4 A cross-sectional view of the crankshaft, cross groove structure, and slider in the diagram;

[0031] Figure 6 It shows Figure 1 A cross-sectional view of the pump body assembly of the compressor in the diagram from a second perspective;

[0032] Figure 7 It shows Figure 6 A cross-sectional structural diagram from the EE perspective;

[0033] Figure 8 It shows Figure 3 A schematic diagram of an alternative embodiment of the upper flange of the pump body assembly;

[0034] Figure 9 It shows Figure 3 A schematic diagram of the upper flange of the pump body assembly having a flow channel;

[0035] Figure 10 It shows Figure 9 A magnified structural diagram at point F in the diagram;

[0036] Figure 11 It shows Figure 9 A cross-sectional view of the exhaust channel and drainage groove of the upper flange in the middle;

[0037] Figure 12 It shows Figure 3 A schematic diagram of an alternative embodiment of the lower flange of the pump body assembly;

[0038] Figure 13 It shows Figure 3 A schematic diagram of the structure of the pump body assembly with a flow channel in the lower flange;

[0039] Figure 14 It shows Figure 13 A magnified structural diagram at point G in the diagram;

[0040] Figure 15 It shows Figure 13 A cross-sectional view of the exhaust channel and drainage groove of the lower flange in the middle;

[0041] Figure 16 It shows Figure 3 A structural diagram showing the angular position of the exhaust passage of the upper flange in the circumferential direction of the upper flange;

[0042] Figure 17 It shows Figure 3 A structural diagram showing the angular position of the exhaust passage of the lower flange in the circumferential direction of the lower flange;

[0043] Figure 18 It shows Figure 3 A schematic diagram of the cylinder liner structure of the pump body assembly;

[0044] Figure 19 It shows Figure 3 A schematic diagram of the upper flange, cylinder liner, and lower flange of the pump body assembly in a disassembled state;

[0045] Figure 20 A schematic diagram of a single-suction cylinder liner pump body structure according to Embodiment 1 of the present invention is shown;

[0046] Figure 21 A schematic diagram of the cylinder liner double intake structure of the pump body according to Embodiment 2 of the present invention is shown;

[0047] Figure 22 A schematic diagram of the upper and lower flanges for air intake in the pump body structure according to Embodiment 3 of the present invention is shown;

[0048] Figure 23 A schematic diagram of the pump body structure according to Embodiment 4 of the present invention is shown.

[0049] Figure 24 It shows Figure 3 A schematic diagram of the eccentricity of the crankshaft shaft body and the two eccentric parts;

[0050] Figure 25 It shows Figure 3 A cross-sectional structural schematic diagram of the assembly eccentricity of the crankshaft and cylinder liner;

[0051] Figure 26 It shows Figure 3 A structural schematic diagram of the eccentricity between the cylinder liner and the lower flange;

[0052] Figure 27 It shows Figure 3 A schematic diagram of the slider in the through hole along its axial direction;

[0053] Figure 28 A schematic diagram illustrating the operating principle of a compressor according to an optional embodiment of the present invention is shown;

[0054] Figure 29 It shows Figure 28 A schematic diagram illustrating the operating principle of the compressor in the diagram;

[0055] Figure 30 A schematic diagram illustrating the operating principle of a compressor in the prior art is shown;

[0056] Figure 31 A schematic diagram illustrating the operating principle of the improved compressor in the prior art is shown;

[0057] Figure 32 It shows Figure 31 The diagram shows the mechanism of the compressor in operation, which illustrates the lever arm that drives the slider to rotate.

[0058] Figure 33 It shows Figure 31 The diagram shows the operating principle of the compressor mechanism. In this diagram, the center of the limiting groove structure and the center of the eccentric part coincide.

[0059] The above figures include the following reference numerals:

[0060] 10. Crankshaft; 11. Eccentric part; 12. Shaft body section;

[0061] 20. Cylinder liner; 21. Radial intake port; 23. Intake chamber; 24. Intake connecting chamber; 27. Bevel cut;

[0062] 30. Cross-groove structure; 31. Limiting channel; 32. Center hole;

[0063] 40. Slider; 41. Through hole; 42. Extrusion surface;

[0064] 50. Flange; 51. Exhaust passage; 52. Upper flange; 53. Lower flange; 54. Intake passage; 58. Drainage channel;

[0065] 80. Dispenser assembly; 81. Housing assembly; 82. Motor assembly; 83. Pump body assembly; 84. Top cover assembly; 85. Bottom cover assembly;

[0066] 90. Fasteners. Detailed Implementation

[0067] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0068] In existing technologies, such as Figure 30 As shown, a compressor operating mechanism principle is proposed based on the cross slider mechanism. Specifically, point O1 is used as the cylinder center, point O2 as the drive shaft center, and point O3 as the slider center. The cylinder and drive shaft are eccentrically set, and the slider center O3 moves in a circle with a diameter of O1O2.

[0069] In the above operating mechanism principle, the cylinder center O1 and the drive shaft center O2 serve as the two rotation centers of the motion mechanism. At the same time, the midpoint O0 of the line segment O1O2 serves as the virtual center of the slider center O3, so that while the slider reciprocates relative to the cylinder, it also reciprocates relative to the drive shaft.

[0070] Because the midpoint O0 of line segment O1O2 is a virtual center, a balancing system cannot be set up, leading to a deterioration of the compressor's high-frequency vibration characteristics. Based on the above operating mechanism principle, as follows... Figure 31 As shown, a motion mechanism with O0 as the center of the drive shaft is proposed. That is, the cylinder center O1 and the drive shaft center O0 are the two rotation centers of the motion mechanism. The drive shaft has an eccentric part, and the slider is coaxially arranged with the eccentric part. The assembly eccentricity of the drive shaft and the cylinder is equal to the eccentricity of the eccentric part, so that the slider center O3 moves in a circle with the drive shaft center O0 as the center and O1O0 as the radius.

[0071] A corresponding operating mechanism is proposed, including a cylinder, a limiting groove structure, a slider, and a drive shaft. The limiting groove structure is rotatably mounted inside the cylinder, and the cylinder and the limiting groove structure are coaxially arranged, that is, the center O1 of the cylinder is also the center of the limiting groove structure. The slider reciprocates relative to the limiting groove structure. The slider is coaxially assembled with the eccentric part of the drive shaft. The slider performs circumferential motion around the shaft body of the drive shaft. Specifically, the motion process is as follows: the drive shaft rotates, causing the slider to revolve around the center of the shaft body of the drive shaft. At the same time, the slider rotates relative to the eccentric part. The slider reciprocates within the limiting groove of the limiting groove structure and pushes the limiting groove structure to rotate.

[0072] However, as Figure 32As shown, the length of the lever arm L that drives the slider to rotate is L = 2e × cosθ × cosθ, where e is the eccentricity of the eccentric part and θ is the angle between the line connecting O1O0 and the sliding direction of the slider in the limiting groove.

[0073] like Figure 33 As shown, when the cylinder center O1 (i.e., the center of the limiting 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 limiting groove structure. That is, the torque applied to the limiting groove structure is zero, the limiting groove structure cannot rotate, and the motion mechanism is at a dead point position and cannot drive the slider to rotate.

[0074] Based on this, this application proposes a novel cross-slot structure with two limiting channels and a double slider mechanism, and constructs a novel compressor based on this principle. This compressor has the characteristics of high energy efficiency and low noise. The following uses the compressor as an example to specifically introduce the compressor based on the cross-slot structure with two limiting channels and the double slider.

[0075] To address the issues of low energy efficiency and high noise levels in existing compressors, as well as the challenges of reducing the processing difficulty of exhaust ports, decreasing clearance volume, and minimizing noise, this invention provides a fluid machine and a heat exchange device. The heat exchange device includes a fluid machine, which is the fluid machine described above and below.

[0076] The fluid machinery of this invention includes a crankshaft 10, a cylinder liner 20, a cross-groove structure 30, and a slider 40. The crankshaft 10 has two eccentric portions 11 arranged along its axial direction, with a phase difference of a first included angle A between them, and the eccentricity of the two eccentric portions 11 is equal. The crankshaft 10 and the cylinder liner 20 are eccentrically arranged with a fixed eccentric distance. The cross-groove structure 30 is rotatably disposed within the cylinder liner 20 and has two limiting channels 31. The two limiting channels 31 are sequentially arranged along the axial direction of the crankshaft 10, and the extending direction of the limiting channels 31 is perpendicular to the axial direction of the crankshaft 10. The extension directions of the positioning channels 31 have a phase difference of a second included angle B, wherein the first included angle A is twice the second included angle B; the slider 40 has a through hole 41, and there are two sliders 40. The two eccentric parts 11 extend into the two through holes 41 of the two sliders 40 respectively. The two sliders 40 are slidably disposed in the two limiting channels 31 and form a variable volume cavity. The variable volume cavity is located in the sliding direction of the slider 40. The crankshaft 10 rotates to drive the slider 40 to slide back and forth in the limiting channel 31 while interacting with the cross groove structure 30, so that the cross groove structure 30 and the slider 40 rotate in the cylinder liner 20.

[0077] By configuring the cross-groove structure 30 into a structure with two limiting channels 31 and correspondingly arranging two sliders 40, the two eccentric portions 11 of the crankshaft extend into the two through holes 41 of the two sliders 40. Simultaneously, the two sliders 40 are slidably disposed within the two limiting channels 31, forming a variable volume cavity. Since the first included angle A between the two eccentric portions 11 is twice the second included angle B between the extending directions of the two limiting channels 31, when one of the two sliders 40 is at a dead position, that is, the driving torque of the eccentric portion 11 corresponding to the slider 40 at the dead position is 0. When the slider 40 is at its dead point, it cannot continue to rotate. At this time, the driving torque of the other eccentric part 11 driving the corresponding slider 40 is at its maximum value, ensuring that the eccentric part 11 with the maximum driving torque can drive the corresponding slider 40 to rotate normally. This slider 40 drives the cross groove structure 30 to rotate, and then the cross groove structure 30 drives the slider 40 at its dead point to continue to rotate. This achieves stable operation of the fluid machinery, avoids the dead point of the motion mechanism, improves the motion reliability of the fluid machinery, and thus ensures the working reliability of the heat exchange equipment.

[0078] Furthermore, since the fluid machinery provided in this application can operate stably, that is, it ensures that the compressor has high energy efficiency and low noise, thereby ensuring the reliability of the heat exchange equipment.

[0079] It should be noted that in this application, neither the first included angle A nor the second included angle B is zero.

[0080] like Figure 28 and Figure 29As shown, when the aforementioned fluid machinery is running, the crankshaft 10 rotates around its axis O0; the cross-groove structure 30 revolves around the axis O0 of the crankshaft 10, with the axis O0 of the crankshaft 10 and the axis O1 of the cross-groove structure 30 being eccentrically positioned with a fixed eccentricity; the first slider 40 moves in a circular motion with the axis O0 of the crankshaft 10 as its center, and the distance between the center O3 of the first slider 40 and the axis O0 of the crankshaft 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 cross-groove structure 30. The crankshaft 10 rotates to drive the first slider 40 to move in a circular motion. The first slider 40 interacts with the cross groove structure 30 and slides back and forth within the limiting channel 31 of the cross groove structure 30; the second slider 40 makes a circular motion 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 eccentricity of the second eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentric distance between the axis O0 of the crankshaft 10 and the axis O1 of the cross groove structure 30. The crankshaft 10 rotates to drive the second slider 40 to make a circular motion, and the second slider 40 interacts with the cross groove structure 30 and slides back and forth within the limiting channel 31 of the cross groove structure 30.

[0081] The fluid machinery operating as described above constitutes a cross-slider mechanism. This operating method adopts the principle of a cross-slider mechanism, wherein the two eccentric portions 11 of the crankshaft 10 serve as the first connecting rod L1 and the second connecting rod L2, respectively, and the two limiting channels 31 of the cross groove structure 30 serve as the third connecting rod L3 and the fourth connecting rod L4, respectively, and the lengths of the first connecting rod L1 and the second connecting rod L2 are equal (please refer to...). Figure 28 ).

[0082] like Figure 28 As shown, there is a first included angle A between the first link L1 and the second link L2, and 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.

[0083] like Figure 29 As shown, the line connecting the axis O0 of crankshaft 10 and the axis O1 of cross groove structure 30 is line O0O1. The first connecting rod L1 has a third included angle C with line O0O1, and the corresponding third connecting rod L3 has a fourth included angle D with line O0O1, wherein the third included angle C is twice the fourth included angle D; the second connecting rod L2 has a fifth included angle E with line O0O1, and the corresponding fourth connecting rod L4 has a sixth included angle F with line O0O1, wherein the fifth included angle E is twice the sixth included angle F; the sum of the third included angle C and the fifth included angle E is the first included angle A, and the sum of the fourth included angle D and the sixth included angle F is the second included angle B.

[0084] Furthermore, the operating method also includes the slider 40 having the same rotational angular velocity relative to the eccentric part 11 as the slider 40 having the same revolution angular velocity around the axis O0 of the crankshaft 10; and the cross groove structure 30 having the same revolution angular velocity around the axis O0 of the crankshaft 10 as the slider 40 having the same rotational angular velocity relative to the eccentric part 11.

[0085] 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 cross-groove structure 30 corresponds to the rotation center of the third connecting rod L3 and the fourth connecting rod L4. The two eccentric parts 11 of the crankshaft 10 serve as the first connecting rod L1 and the second connecting rod L2, respectively, and the two limiting channels 31 of the cross-groove structure 30 serve as the third connecting rod L3 and the fourth connecting rod L4, respectively. The lengths of the first connecting rod L1 and the second connecting rod L2 are equal. Thus, while the crankshaft 10 rotates, the eccentric parts 11 on the crankshaft 10 drive the corresponding sliders 40 to revolve around the axis O0 of the crankshaft 10. At the same time, the sliders 40 can rotate relative to the eccentric parts 11, and the relative rotation speeds of the two are the same. Since the first slider 40 and the second slider 40 are respectively at two corresponding limiting channels... The reciprocating motion within channel 31 drives the cross-groove structure 30 to perform circular motion. Limited by the two limiting channels 31 of the cross-groove structure 30, the movement directions of the two sliders 40 always have a phase difference of the second included angle B. When one of the two sliders 40 is at the dead point position, the eccentric part 11 used to drive the other slider 40 has the maximum driving torque. The eccentric part 11 with the maximum driving torque can normally drive the corresponding slider 40 to rotate, thereby driving the cross-groove structure 30 to rotate, and then driving the slider 40 at the dead point position to continue rotating through the cross-groove structure 30. This achieves stable operation of the fluid machinery, avoids the dead point position of the motion mechanism, improves the motion reliability of the fluid machinery, and thus ensures the working reliability of the heat exchange equipment.

[0086] It should be noted that, in this application, the maximum lever arm of the driving torque of the eccentric part 11 is 2e.

[0087] Under this motion method, the trajectory of slider 40 is a circle, with the axis O0 of crankshaft 10 as the center and the line O0O1 as the radius.

[0088] It should be noted that in this application, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 revolutions, completing 4 intake and exhaust processes.

[0089] like Figures 1 to 27As shown, the fluid machinery also includes a flange 50, which is located at the axial end of the cylinder liner 20. The crankshaft 10 is concentrically arranged with the flange 50, and the cross groove structure 30 is coaxially arranged with the cylinder liner 20. The assembly eccentricity of the crankshaft 10 and the cross groove structure 30 is determined by the relative positional relationship between the flange 50 and the cylinder liner 20. The flange 50 is fixed to the cylinder liner 20 by fasteners 90. The relative position of the axis of the flange 50 and the axis of the inner ring of the cylinder liner 20 is controlled by the flange 50 self-aligning. 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 self-aligning 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.

[0090] Specifically, such as Figure 24 As shown, the eccentricity of both eccentric parts 11 is equal to e, as... Figure 25 As shown, the assembly eccentricity between crankshaft 10 and cylinder liner 20 is e (since the cross-groove structure 30 and cylinder liner 20 are coaxially arranged, the assembly eccentricity between crankshaft 10 and cross-groove structure 30 is the same as the assembly eccentricity between crankshaft 10 and cylinder liner 20). Flange 50 includes upper flange 52 and lower flange 53, as shown... Figure 26 As shown, the distance between the inner ring axis of the cylinder liner 20 and the inner ring axis of the lower flange 53 is e, which is equal to the eccentricity of the eccentric part 11.

[0091] Optionally, a first assembly gap is provided between the crankshaft 10 and the flange 50, the first assembly gap being in the range of 0.005mm to 0.05mm.

[0092] Preferably, the range of the first assembly gap is 0.01 to 0.03 mm.

[0093] Optionally, the two sliders 40 are respectively concentrically arranged with the two eccentric parts 11. The sliders 40 move in a circular motion around the axis of the crankshaft 10. There is a first rotational gap between the hole wall of the through hole 41 and the eccentric part 11. The range of the first rotational gap is 0.005mm to 0.05mm.

[0094] Optionally, a second rotational clearance is provided between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder liner 20, the size of which is 0.005mm to 0.1mm.

[0095] like Figures 1 to 5 , Figure 7 , Figures 20 to 24 As shown, the crankshaft 10 has a single integral shaft body 12, and the shaft body 12 has only one shaft center. This facilitates the one-time molding of the shaft body 12, thereby reducing the difficulty of machining and manufacturing the shaft body 12.

[0096] It should be noted that, in an embodiment of this application not shown, 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 coaxially arranged, and two eccentric portions 11 are respectively arranged on the first section and the second section.

[0097] Optionally, the first and second sections can be detachably connected. This ensures ease of assembly and disassembly of the crankshaft 10.

[0098] like Figures 1 to 5 , Figure 7 , Figures 20 to 24 As shown, the shaft body portion 12 and the eccentric portion 11 of the crankshaft 10 are integrally formed. This facilitates the one-time forming of the crankshaft 10, thereby reducing the difficulty of machining and manufacturing the crankshaft 10.

[0099] It should be noted that, in an embodiment not shown in this application, the shaft portion 12 of the crankshaft 10 is detachably connected to the eccentric portion 11. This facilitates the installation and removal of the eccentric portion 11.

[0100] like Figure 3 and Figure 4 As shown, both ends of the limiting channel 31 extend to the outer peripheral surface of the cross groove structure 30. This helps to reduce the processing and manufacturing difficulty of the cross groove structure 30.

[0101] It should be noted that in this application, the first included angle A is 160 degrees to 200 degrees; the second included angle B is 80 degrees to 100 degrees. Thus, it is sufficient to satisfy the relationship that the first included angle A is twice the second included angle B.

[0102] Preferably, the first included angle A is 160 degrees and the second included angle B is 80 degrees.

[0103] Preferably, the first included angle A is 165 degrees and the second included angle B is 82.5 degrees.

[0104] Preferably, the first included angle A is 170 degrees and the second included angle B is 85 degrees.

[0105] Preferably, the first included angle A is 175 degrees and the second included angle B is 87.5 degrees.

[0106] Preferably, the first included angle A is 180 degrees and the second included angle B is 90 degrees.

[0107] Preferably, the first included angle A is 185 degrees and the second included angle B is 92.5 degrees.

[0108] Preferably, the first included angle A is 190 degrees and the second included angle B is 95 degrees.

[0109] Preferably, the first included angle A is 195 degrees and the second included angle B is 97.5 degrees.

[0110] It should be noted that in this 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. This ensures that the arc surface of the eccentric portion 11 can apply an effective driving force to the slider 40, thereby ensuring the reliability of the slider 40's movement.

[0111] like Figures 1 to 5 , Figure 7 , Figures 20 to 24 As shown, the eccentric part 11 is cylindrical.

[0112] Optionally, the proximal end of the eccentric portion 11 is flush with the outer circle of the shaft portion 12 of the crankshaft 10.

[0113] Optionally, the proximal end of the eccentric portion 11 protrudes beyond the outer circle of the shaft portion 12 of the crankshaft 10.

[0114] Optionally, the proximal end of the eccentric portion 11 is located inside the outer circle of the shaft portion 12 of the crankshaft 10.

[0115] It should be noted that, in one embodiment of this application (not shown), the slider 40 includes multiple substructures, which are spliced ​​together to form a through hole 41.

[0116] like Figures 1 to 5 , Figure 7 , Figures 20 to 24 As shown, the two eccentric portions 11 are spaced apart axially on the crankshaft 10. This ensures that during the assembly of the crankshaft 10, cylinder liner 20, and two sliders 40, the spacing between the two eccentric portions 11 provides sufficient assembly space for the cylinder liner 20, thus ensuring ease of assembly.

[0117] like Figure 3 As shown, the cross-groove structure 30 has a central hole 32, through which two limiting channels 31 are connected. The diameter of the central hole 32 is larger than the diameter of the shaft portion 12 of the crankshaft 10. This ensures that the crankshaft 10 can pass smoothly through the central hole 32.

[0118] Optionally, the diameter of the central hole 32 is larger than the diameter of the eccentric portion 11. This ensures that the eccentric portion 11 of the crankshaft 10 can pass smoothly through the central hole 32.

[0119] like Figure 27As shown, the projection of slider 40 in the axial direction of 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 opposing first sliding surfaces that slide in contact with slider 40. Slider 40 has a second sliding surface that mates with the first sliding surface. Slider 40 has a pressing surface 42 facing the end of limiting channel 31, which serves as the head of slider 40. The two second sliding surfaces are connected by the pressing surface 42, which faces the variable volume cavity. Thus, the projection of the second sliding surface of slider 40 in the axial direction of its through hole 41 is a straight line segment, while the projection of the pressing surface 42 of slider 40 in the axial direction of its through hole 41 is an arc segment.

[0120] Specifically, the extrusion surface 42 is an arc surface, and the distance between the center of the arc surface and the center of the through hole 41 is equal to the eccentricity of the eccentric part 11. Figure 27 In the middle, the center of the through hole 41 of the slider 40 is O. 滑块 The distance between the center of the two arc surfaces and the center of the through hole 41 is 'e', ​​that is, the eccentricity of the eccentric part 11. Figure 27 The dashed X-line in the diagram represents the circle containing the center of the two arc surfaces.

[0121] Optionally, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner 20.

[0122] Optionally, the radius of curvature of the arc surface has a difference from the radius of the inner circle of the cylinder liner 20, and the difference ranges from -0.05mm to 0.025mm.

[0123] Preferably, the difference ranges from -0.02 to 0.02 mm.

[0124] It should be noted that in this application, the projected area S of the extrusion surface 42 in the sliding direction of the slider 40 is... 滑块 The area S of the compression exhaust port 22 of cylinder liner 20 排 The following conditions must be met between them: S 滑块 / S 排 The value is 8 to 25.

[0125] Preferably, S 滑块 / S 排 The value is 12 to 18.

[0126] It should be noted that the fluid machinery shown in this embodiment is a compressor, such as... Figure 1As shown, the compressor includes a distributor component 80, a housing assembly 81, a motor assembly 82, a pump body assembly 83, an upper cover assembly 84, and a lower cover assembly 85. The distributor component 80 is located outside the housing assembly 81. The upper cover assembly 84 is mounted on the upper end of the housing assembly 81, and the lower cover assembly 85 is mounted on the lower end of the housing assembly 81. The motor assembly 82 and the pump body assembly 83 are both located inside the housing assembly 81, with the motor assembly 82 located either above or below the pump body assembly 83. The pump body assembly 83 of the compressor includes the aforementioned crankshaft 10, cylinder liner 20, cross-groove structure 30, slider 40, upper flange 52, and lower flange 53.

[0127] Alternatively, the above-mentioned components can be connected by welding, heat fitting, or cold pressing.

[0128] 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 channels 31, the two eccentric parts 11 of the crankshaft 10 are respectively inserted into the two through holes 41 of the corresponding two sliders 40, and then the assembled crankshaft 10, cross groove structure 30 and two sliders 40 are placed in the cylinder liner 20. One end of the crankshaft 10 is installed on the lower flange 53, and the other end of the crankshaft 10 is set through the upper flange 52. For details, please refer to [link to documentation]. Figure 2 and Figure 3 .

[0129] It should be noted that in this embodiment, the enclosed space formed by the slider 40, the limiting channel 31, the cylinder liner 20 and the upper flange 52 (or lower flange 53) is the variable volume chamber. The pump body assembly 83 has a total of 4 variable volume chambers. During the rotation of the crankshaft 10, the crankshaft 10 rotates 2 revolutions, and a single variable volume chamber completes 1 intake and exhaust process. For the compressor, the crankshaft 10 rotates 2 revolutions, and a total of 4 intake and exhaust processes are completed.

[0130] Furthermore, the enclosed space formed by the extrusion surface 42 of the head of the slider 40, the two side walls and the bottom surface of the limiting channel 31, part of the inner wall of the cylinder liner 20, and part of the surface of the upper flange 52 facing the cylinder liner 20 (or part of the surface of the lower flange 53 facing the cylinder liner 20) is the variable volume cavity.

[0131] The following is a detailed introduction to the operation of the compressor:

[0132] like Figure 1As shown, the motor assembly 82 drives the crankshaft 10 to rotate. The two eccentric parts 11 of the crankshaft 10 drive the corresponding two sliders 40 to move. While the sliders 40 revolve around the axis of the crankshaft 10, the sliders 40 rotate relative to the eccentric parts 11. The sliders 40 reciprocate along the limiting channel 31 and drive the cross groove structure 30 to rotate inside the cylinder liner 20. The sliders 40 revolve along the limiting channel 31 while revolving, thus forming the cross slider mechanism motion mode.

[0133] To address the issues of reducing the machining difficulty of parts, decreasing clearance volume, and reducing noise, this application improves the exhaust structure of the exhaust channels 51 by respectively setting two exhaust channels 51 on two flanges 50, thus transforming the exhaust channels 51 from the existing cylinder liner 20 sidewall exhaust structure into a planar exhaust structure, as detailed below:

[0134] like Figures 1 to 27 As shown, the fluid machinery includes two flanges 50, which are respectively located at both ends of the cylinder liner 20. Each flange 50 is provided with an exhaust passage 51, which is connected to the variable volume cavity on the corresponding side. The cross-sectional area of ​​the exhaust passage 51 is 0.5%-35% of the projected area of ​​the slider 40 in its sliding direction.

[0135] By opening exhaust channels 51 on both flanges 50, and having each exhaust channel 51 connected to the corresponding variable volume cavity, the exhaust channels 51 are located on the plane of the flanges 50. Compared to the existing exhaust channels located on the side wall arc surface of the cylinder liner 20, this reduces the noise caused by the sharp edges of the exhaust channels 51 and misalignment during assembly of the cylinder liner 20 and the flanges 50. This changes the exhaust path of the compressor to avoid noise generation. Furthermore, since the exhaust channels 51 are located on the plane of the flanges 50 and are on the outer plane, the machining difficulty of the exhaust channels 51 is greatly reduced compared to the exhaust channels located on the side wall arc surface of the cylinder liner 20. This makes the parts easier to process and facilitates the removal of burrs or flanging caused by machining.

[0136] Furthermore, since both ends of the exhaust passage 51 of the compressor provided in this application are flat in the length direction, under the condition that the bearing thickness and the diameter of the exhaust passage 51 are the same, the volume of the flat exhaust passage 51 of this application is smaller and the clearance volume is also smaller, which is beneficial to ensuring the cooling capacity and reducing power consumption.

[0137] In addition, exhaust loss can be avoided by reasonably optimizing the cross-sectional area of ​​the exhaust channel 51 and the proportion of the projected area of ​​the slider 40 in its sliding direction.

[0138] It should be noted that the gas compressed in the upper compression chamber of this application is discharged through the upper flange 52, and the gas compressed in the lower compression chamber is discharged through the lower flange 53. The two compression chambers and the two exhaust channels 51 are independent of each other and do not affect each other. This helps to prevent the gas in the two compression chambers from affecting each other and generating noise such as pulsation due to exhaust through the cylinder liner 20 side.

[0139] It should be noted that the existing cylinder liner 20 side exhaust is an indirect exhaust, that is, after the gas is discharged, it first enters the exhaust chamber of the cylinder liner 20 through the exhaust port of the cylinder liner 20, then flows to the flange 50 through the intake connecting chamber on the cylinder liner 20, and finally is discharged from the flange 50. During the entire exhaust process, it passes through the corners or uneven edges left during the assembly of various parts, which is prone to generating noise. In contrast, the exhaust provided in this application through the two exhaust channels 51 on the two flanges 50 is a direct exhaust, in which the gas is directly discharged into the housing. The exhaust path is shorter and less likely to generate turbulent airflow.

[0140] Furthermore, in the existing capless cylinder liner exhaust method, compressed gas is discharged from the side exhaust port of the cylinder liner and directly impacts the shell wall, causing vibration and noise. However, the exhaust method provided in this application, which uses two exhaust channels 51 on two flanges 50, is a direct exhaust method, which can reduce or even eliminate the shortcomings of the cylinder liner side exhaust method and greatly reduce the harm of vibration and noise.

[0141] like Figure 5 As shown, the projection of slider 40 in its sliding direction is a semicircle.

[0142] like Figure 16 and Figure 17 As shown, the structural schematic diagram shows the angular positions of the two exhaust channels 51 in the circumferential direction of the upper flange 52 and the lower flange 53, respectively. 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.

[0143] Specifically, such as Figure 16 As shown, the exhaust passage 51 of the assembled upper flange 52 is positioned in the circumferential direction of the upper flange 52 with the starting angle of the upper slider 40 for intake as the baseline of 0° and the clockwise rotation angle as positive. The setting position of the exhaust passage 51 in the circumferential direction of the upper flange 52 is within the angle range of (90°-arccos(C / D)~90°+arccos(C / D)), where C is the distance between two relatively parallel straight line segments projected by the slider 40 in the axial direction of the through hole 41, and D is the inner diameter of the cylinder liner 20.

[0144] Furthermore, such as Figure 17As shown, the exhaust passage 51 of the assembled lower flange 53 is positioned in the circumferential direction of the lower flange 53 with the angle at which the lower slider 40 begins to draw air as the baseline of 0° and the clockwise rotation angle as positive. The setting position of the exhaust passage 51 in the circumferential direction of the lower flange 53 is within the angle range of (90°-arccos(C / D)~90°+arccos(C / D)), where C is the distance between two relatively parallel straight line segments projected by the slider 40 in the axial direction of the through hole 41, and D is the inner diameter of the cylinder liner 20.

[0145] like Figures 16 to 19 As shown, oblique cuts 27 are provided at the inner edges of both ends of the cylinder liner 20 along its axial direction. The two oblique cuts 27 are used to connect with the two exhaust passages 51 respectively. In this way, the oblique cuts 27 help to increase the gas flow path, thereby reducing exhaust losses.

[0146] like Figures 16 to 19 As shown, the two exhaust passages 51 are concentrically arranged in the axial direction of the cylinder liner 20, and the two oblique cuts 27 are in the same position in the circumferential direction of the cylinder liner 20.

[0147] Of course, in an embodiment of this application not shown, the two exhaust passages 51 are not concentrically arranged in the axial direction of the cylinder liner 20, and the two oblique cuts 27 are not in the circumferential direction of the cylinder liner 20.

[0148] It should be noted that, in this application, the sum of the projected area of ​​the oblique cut 27 on the inner circle of the cylinder liner 20 and the projected area of ​​the oblique cut 27 on the end face of the cylinder liner 20 is greater than or equal to the cross-sectional area of ​​the exhaust passage 51. This helps to increase the gas flow path, thereby reducing exhaust losses.

[0149] It should be noted that, in this application, in order to reduce overcompression and power consumption, a drainage groove 58 is provided on the end face of the flange 50 facing the cylinder liner 20. The drainage groove 58 is connected to the exhaust channel 51, and the drainage groove 58 is opposite to and connected to the oblique cut 27. In this way, while reducing overcompression and power consumption, it also serves as a resonant cavity.

[0150] Specifically, such as Figure 8 As shown in the diagram, the upper flange 52 does not have a drainage groove 58; Figures 9 to 11 The diagram shows a structure in which a drainage groove 58 is provided on the end face of the upper flange 52 facing the cylinder liner 20.

[0151] Specifically, such as Figure 12 As shown in the schematic diagram, the lower flange 53 does not have a drainage groove 58; as Figures 13 to 14 The diagram shows a structure in which a drainage groove 58 is provided on the end face of the upper flange 52 facing the cylinder liner 20.

[0152] It should be noted that in this application, the cylinder liner 20 has at least one radial intake port 21, which communicates with the variable volume chamber. The inner wall of the cylinder liner 20 has an intake chamber 23, and the radial intake port 21 communicates with the variable volume chamber through the intake chamber 23. This ensures that the intake chamber 23 can store a large amount of gas, allowing the variable volume chamber to be fully saturated, thus enabling the compressor to draw in sufficient gas. Furthermore, when intake is insufficient, the stored gas can be supplied to the variable volume chamber in a timely manner to ensure the compressor's compression efficiency. In addition, sufficient compressor intake, as well as the compressor's performance and cooling capacity, can be improved. This solves the problem of interference between various structures during design due to the compact structure of the pump assembly 83, making the design easier.

[0153] Optionally, the intake chamber 23 is a cavity formed by radially hollowing out the inner wall surface of the cylinder liner 20. There can be one intake chamber 23 or two chambers, one above the other.

[0154] Specifically, the intake chamber 23 extends circumferentially around the inner wall of the cylinder liner 20 by a first predetermined distance to form an arc-shaped intake chamber 23. This ensures that the volume of the intake chamber 23 is large enough to store a large amount of gas.

[0155] Example 1

[0156] like Figure 20 As shown, there are two intake chambers 23, which are spaced apart along the axial direction of the cylinder liner 20. The cylinder liner 20 also has an intake connecting chamber 24, and both intake chambers 23 are connected to the intake connecting chamber 24. When the cylinder liner 20 has a radial intake hole 21, the radial intake hole 21 is connected to both intake chambers 23 through the intake connecting chamber 24. This helps to increase the volume of the intake chambers 23, thereby reducing intake pressure pulsation.

[0157] Furthermore, the intake communication cavity 24 extends along the axial direction of the cylinder liner 20 by a second predetermined distance, and at least one end of the intake communication cavity 24 penetrates the axial end face of the cylinder liner 20. This facilitates the opening of the intake communication cavity 24 from the end face of the cylinder liner 20, ensuring the ease of machining the intake communication cavity 24.

[0158] Example 2

[0159] like Figure 21 As shown, there are two intake chambers 23, which are spaced apart along the axial direction of the cylinder liner 20. There are two radial intake holes 21, which correspond one-to-one with the two intake chambers 23. The two radial intake holes 21 are connected to the corresponding variable volume chambers through the two intake chambers 23 respectively.

[0160] Example 3

[0161] like Figure 22As shown, one of the two flanges 50 has an intake passage 54, and the intake passage 54 and the exhaust passage 51 on the same flange 50 have a phase difference in the circumferential direction of the flange 50. The cylinder liner 20 has a radial intake port 21, and the intake passage 54 and the radial intake port 21 are respectively connected to two variable volume chambers.

[0162] Example 4

[0163] like Figure 23 As shown, both flanges 50 have an intake passage 54, and the intake passage 54 and the exhaust passage 51 on the same flange 50 have a phase difference in the circumferential direction of the flange 50. The two intake passages 54 are respectively connected to two variable volume chambers.

[0164] It should be noted that, in this application, if Figure 3 As shown, both flanges 50 are connected to the cylinder liner 20 by fasteners 90.

[0165] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0166] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0167] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0168] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0169] It should be noted that the terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in sequences other than those illustrated or described herein.

[0170] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A fluid machine, characterized in that, include: A crankshaft (10) having two eccentric portions (11) along its axial direction; Cylinder liner (20), the crankshaft (10) and the cylinder liner (20) are eccentrically arranged and the eccentric distance is fixed; A cross-groove structure (30) is rotatably disposed within the cylinder liner (20). The cross-groove structure (30) has two limiting channels (31), which are arranged sequentially 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). The slider (40) has a through hole (41). There are two sliders (40). The two eccentric parts (11) extend into the two through holes (41) of the two sliders (40). The two sliders (40) are slidably disposed in the two limiting channels (31) and form a variable volume cavity. The variable volume cavity is located in the sliding direction of the slider (40). The crankshaft (10) rotates to drive the slider (40) to slide back and forth in the limiting channel (31) while interacting with the cross groove structure (30), so that the cross groove structure (30) and the slider (40) rotate in the cylinder liner (20). Two flanges (50) are respectively disposed at both ends of the cylinder liner (20). Each of the two flanges (50) is provided with an exhaust passage (51), and the two exhaust passages (51) are respectively connected to the variable volume cavity on the corresponding side. Wherein, the cross-sectional area of ​​the exhaust channel (51) is 0.5%-35% of the projected area of ​​the slider (40) in its sliding direction; The slider (40) has two relatively parallel straight line segments and an arc segment connecting the ends of the two straight line segments in the axial projection of the through hole (41). The exhaust passage (51) is positioned on the flange (50) in the circumferential direction within the angular range of (90°-arccos(C / D)~90°+arccos(C / D)), where C is the distance between two relatively parallel straight line segments projected by the slider (40) in the axial direction of the through hole (41), and D is the inner diameter of the cylinder liner (20).

2. The fluid machinery according to claim 1, characterized in that, The projection of the slider (40) in its sliding direction is a semicircle.

3. The fluid machinery according to claim 1, characterized in that, The cylinder liner (20) has oblique cuts (27) at the inner edges of both ends of the cylinder liner (20) along its axial direction. The two oblique cuts (27) are used to communicate with the two exhaust passages (51).

4. The fluid machinery according to claim 3, characterized in that, The two exhaust passages (51) are concentrically arranged in the axial direction of the cylinder liner (20), and the two oblique cuts (27) are aligned in the circumferential direction of the cylinder liner (20); or, The two exhaust passages (51) are not concentrically arranged in the axial direction of the cylinder liner (20), and the two oblique cuts (27) are not in the same position in the circumferential direction of the cylinder liner (20).

5. The fluid machinery according to claim 3, characterized in that, The sum of the projected area of ​​the oblique cut (27) on the inner circle of the cylinder liner (20) and the projected area of ​​the oblique cut (27) on the end face of the cylinder liner (20) is greater than or equal to the cross-sectional area of ​​the exhaust passage (51).

6. The fluid machinery according to claim 3, characterized in that, The flange (50) has a drainage groove (58) on the end face facing the cylinder liner (20). The drainage groove (58) is connected to the exhaust channel (51). The drainage groove (58) is opposite to and connected to the oblique cut (27).

7. The fluid machinery according to claim 1, characterized in that, The cylinder liner (20) has at least one radial intake hole (21) for communicating with the variable volume cavity. The inner wall surface of the cylinder liner (20) has an intake cavity (23), and the radial intake hole (21) communicates with the variable volume cavity through the intake cavity (23).

8. The fluid machinery according to claim 7, characterized in that, The intake chamber (23) extends circumferentially around the inner wall of the cylinder liner (20) by a first preset distance to form an arc-shaped intake chamber (23).

9. The fluid machinery according to claim 7, characterized in that, There are two intake chambers (23), which are spaced apart along the axial direction of the cylinder liner (20). The cylinder liner (20) also has an intake communication chamber (24), and both intake chambers (23) are connected to the intake communication chamber (24). When the cylinder liner (20) has a radial intake hole (21), the radial intake hole (21) is connected to the two intake chambers (23) through the intake communication chamber (24).

10. The fluid machinery according to claim 9, characterized in that, The intake communication cavity (24) extends a second preset distance along the axial direction of the cylinder liner (20), and at least one end of the intake communication cavity (24) penetrates the axial end face of the cylinder liner (20).

11. The fluid machinery according to claim 7, characterized in that, There are two intake chambers (23), which are spaced apart along the axial direction of the cylinder liner (20). There are two radial intake holes (21), which correspond one-to-one with the two intake chambers (23). The two radial intake holes (21) are connected to the corresponding variable volume chambers through the two intake chambers (23).

12. The fluid machinery according to claim 7, characterized in that, One of the two flanges (50) has an intake passage (54), and the intake passage (54) and the exhaust passage (51) on the same flange (50) have a phase difference in the circumferential direction of the flange (50). The cylinder liner (20) has a radial intake port (21), and the intake passage (54) and the radial intake port (21) are respectively connected to the two variable volume chambers.

13. The fluid machinery according to claim 7, characterized in that, Both flanges (50) have an air intake passage (54), and the air intake passage (54) and the exhaust passage (51) on the same flange (50) have a phase difference in the circumferential direction of the flange (50). The two air intake passages (54) are respectively connected to the two variable volume cavities.

14. The fluid machinery according to any one of claims 1 to 13, characterized in that, There is a phase difference of a first included angle A between the two eccentric portions (11), the eccentricity of the two eccentric portions (11) is equal, 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.

15. A heat exchange device, comprising fluid machinery, characterized in that, The fluid machinery is the fluid machinery according to any one of claims 1 to 14.

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