Fluid machine and heat exchange device

Abstract

The application provides a fluid machine and a heat exchange device, and the fluid machine comprises a crankshaft, a cylinder sleeve, a cross groove structure and a sliding block, the crankshaft is provided with two eccentric parts along the axial direction of the crankshaft; the crankshaft is eccentrically arranged with the cylinder sleeve and the eccentric distance is fixed; the cross groove structure is rotatably arranged in the cylinder sleeve and coaxially arranged with the cylinder sleeve, a first radial gap C1 is formed between the outer circumferential surface of the cross groove structure and the inner wall surface of the cylinder sleeve, the range of the first radial gap C1 is 0.01-0.08 mm, two limiting channels of the cross groove structure are sequentially arranged along the axial direction of the crankshaft, and the extending direction of the limiting channels is perpendicular to the axial direction of the crankshaft; the two eccentric parts correspondingly extend into two through holes of the two sliding blocks, the two sliding blocks are correspondingly arranged in the two limiting channels and form a variable volume cavity, and the variable volume cavity is located in the sliding direction of the sliding block. The application solves the problems of low energy efficiency, large noise and how to ensure that the comprehensive efficiency of the compressor reaches the optimal in the prior art.

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, considering that the gaps between the various friction pairs of the compressor have a significant impact on its energy efficiency, the larger the gap between the friction pairs, the lower the power consumption of the friction pairs and the higher the mechanical efficiency of the compressor; however, excessive gaps can lead to leakage, resulting in a decrease in the volumetric efficiency of the compressor. Therefore, it is necessary to design the gaps at various points of the compressor in a reasonable manner to ensure that the overall efficiency of the compressor can reach the optimal level. 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 ensure that the overall efficiency of the compressor is optimal.

[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, and a slider, wherein the crankshaft has two eccentric portions arranged along its axial direction; the crankshaft and the cylinder liner are eccentrically arranged with a fixed eccentric distance; the cross-groove structure is rotatably disposed within the cylinder liner and is coaxially arranged with the cylinder liner, and a first radial clearance C1 is formed between the outer peripheral surface of the cross-groove structure and the inner wall surface of the cylinder liner, the first radial clearance C1 being in the range of 0.01 to 0.08 mm; the cross-groove structure has two limiting channels, the two limiting channels being sequentially arranged along the axial direction of the crankshaft, and the extending direction of the limiting channels being perpendicular to the axial direction of the crankshaft; the slider has through holes, there are two sliders, the two eccentric portions correspondingly extend 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 slider to reciprocate within the limiting channels while interacting with the cross-groove structure, causing the cross-groove structure and the slider to rotate within the cylinder liner.

[0007] Furthermore, the first radial clearance C1 ranges from 0.015 to 0.03 mm.

[0008] Furthermore, the cross-groove structure has a central hole through which two limiting channels are connected, and the diameter of the central hole is larger than the diameter of the crankshaft shaft portion.

[0009] Furthermore, the diameter of the central hole is larger than the diameter of the eccentric part, and there is a second radial gap C2 between the hole wall surface of the central hole and the outer peripheral surface of the eccentric part, the range of the second radial gap C2 being 0.05 to 1 mm.

[0010] Furthermore, the inner diameter D of the cylinder liner 缸套 With the outer diameter d of the cross groove structure 槽 The following conditions must be met: D 缸套 =d 槽 +2C1; Diameter D of the center hole 限 With respect to the diameter d of the eccentric part 偏 The following conditions must be met: D 限 =d 偏 +2C2.

[0011] Furthermore, the slider has an extrusion surface facing the end of the limiting channel, which serves as the head of the slider and faces the variable volume cavity; the extrusion surface is an arc surface, and there is a sealing distance M between the top of the arc surface and the hole wall of the central hole, and the sealing distance M changes periodically as the slider slides in the limiting channel.

[0012] Furthermore, the sealing distance M has a minimum sealing distance M 最小 Minimum sealing distance M 最小 The range is 1 to 6 mm.

[0013] Furthermore, the minimum sealing distance M 最小 The range is 2 to 4 mm.

[0014] Furthermore, the sealing distance M has a minimum sealing distance M 最小 The outer diameter d of the cross groove structure 槽 The diameter D of the center hole 限 The eccentricity e of the eccentric part satisfies: d 槽 =D 限 +8e+2M 最小 .

[0015] Furthermore, the eccentric part is cylindrical, with its proximal end protruding beyond the outer circle of the crankshaft's shaft body.

[0016] Furthermore, the protrusion T at the proximal end of the eccentric portion satisfies: T > 0.

[0017] Furthermore, the protrusion T at the proximal end of the eccentric portion ranges from 0.1 to 2 mm.

[0018] Furthermore, the protrusion T at the proximal end of the eccentric portion and the diameter d of the eccentric portion...偏 The diameter d of the shaft section 轴 The eccentricity e of the eccentric part satisfies: d 偏 =d 轴 +2e+2T.

[0019] 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.

[0020] 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.

[0021] By applying the technical solution of this invention, based on the principle of optimal comprehensive efficiency of fluid machinery, the radial dimension relationship of the pump body component of the fluid machinery is clarified, and the scheme is optimized for each design variable that affects the radial dimension, thereby ensuring that the mechanical efficiency and volumetric efficiency of the fluid machinery are both within a better range, and thus ensuring the optimal comprehensive energy efficiency of the fluid machinery.

[0022] Furthermore, considering that during the operation of the fluid machinery, the first radial gap C1 between the outer peripheral surface of the cross groove structure and the inner wall surface of the cylinder liner will be filled with lubricating oil, making the lubrication between the cross groove structure and the cylinder liner a hydrodynamic lubrication. Under hydrodynamic lubrication, the larger the gap, the greater the frictional power consumption, and the higher the mechanical efficiency of the fluid machinery. At the same time, during the operation of the fluid machinery, there is a pressure difference between the gas at the ends of the slider on both sides of its sliding direction. The side connected to the intake channel is the intake pressure, and the other end is the intermediate pressure or exhaust pressure during the compression process. The gas leaks from the high-pressure side to the low-pressure side through the first radial gap C1 between the cross groove structure and the cylinder liner. The smaller the gap on the low-pressure side, the better the sealing performance, the smaller the leakage, and the higher the volumetric efficiency of the fluid machinery.

[0023] In summary, the first radial clearance C1 has opposite effects on mechanical efficiency and volumetric efficiency. Through theoretical analysis and experimental verification, optimizing the range of the first radial clearance C1 to be within the range of 0.01 to 0.08 mm can improve the overall efficiency of fluid machinery. Attached Figure Description

[0024] 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:

[0025] Figure 1 A schematic diagram of the internal structure of a compressor according to an optional embodiment of the present invention is shown;

[0026] Figure 2 It shows Figure 1 A schematic diagram of the pump body assembly of the compressor in the image;

[0027] Figure 3 It shows Figure 2 An exploded view of the pump body components;

[0028] Figure 4 It shows Figure 3 A schematic diagram of the cylinder liner structure of the pump body assembly;

[0029] Figure 5 It shows Figure 3 A schematic diagram of the cross-groove structure of the pump body assembly;

[0030] Figure 6 It shows Figure 3 A schematic diagram of the eccentricity of the crankshaft shaft body and the two eccentric parts;

[0031] Figure 7 It shows Figure 6 A magnified structural diagram at point F in the diagram;

[0032] Figure 8 It shows Figure 3 A schematic diagram of the sealing distance M between the top of the extrusion surface of the slider head of the pump body assembly and the hole wall of the central hole of the cross groove structure.

[0033] Figure 9 It shows Figure 3 A schematic diagram of the sealing distance M between the top of the extrusion surface of the slider head of the pump body assembly and the hole wall of the central hole of the cross groove structure.

[0034] Figure 10 It shows Figure 3 A schematic diagram of the pump body assembly when the cylinder liner and lower flange are in a disassembled state;

[0035] Figure 11 It shows Figure 10 A structural schematic diagram of the eccentricity between the cylinder liner and the lower flange;

[0036] Figure 12 It shows Figure 3 A cross-sectional structural schematic diagram of the assembly eccentricity of the crankshaft and cylinder liner;

[0037] Figure 13 It shows Figure 3 A schematic diagram of the slider in the through hole along its axial direction;

[0038] Figure 14 It shows Figure 3A schematic diagram of the compressor in the intake state.

[0039] Figure 15 It shows Figure 3 A schematic diagram of the compressor in the intake process.

[0040] Figure 16 It shows Figure 3 A schematic diagram of the compressor in the state at the end of the intake phase;

[0041] Figure 17 It shows Figure 3 A schematic diagram of the compressor's state when it is compressing gas;

[0042] Figure 18 It shows Figure 3 A schematic diagram of the compressor in the exhaust process.

[0043] Figure 19 It shows Figure 3 A schematic diagram of the compressor in the state at the end of exhaust;

[0044] Figure 20 A schematic diagram illustrating the operating principle of a compressor according to an optional embodiment of the present invention is shown;

[0045] Figure 21 It shows Figure 20 A schematic diagram illustrating the operating principle of the compressor in the diagram;

[0046] Figure 22 A schematic diagram illustrating the operating principle of a compressor in the prior art is shown;

[0047] Figure 23 A schematic diagram illustrating the operating principle of the improved compressor in the prior art is shown;

[0048] Figure 24 It shows Figure 23 The diagram shows the mechanism of the compressor in operation, which illustrates the lever arm that drives the slider to rotate.

[0049] Figure 25 It shows Figure 23 The schematic diagram of the compressor's operating mechanism shows that the center of the limiting groove structure and the center of the eccentric part coincide.

[0050] Figure 26 The graph shows the effect of the first radial clearance C1 on the various efficiencies of the compressor;

[0051] Figure 27 A graph showing the effect of the second radial clearance C2 on the mechanical efficiency of the compressor is shown.

[0052] Figure 28 The graphs showing the effect of minimum seal distance on various efficiencies of the compressor are shown.

[0053] Figure 29 A graph showing the effect of minimum protrusion on the mechanical efficiency of the compressor is presented.

[0054] The above figures include the following reference numerals:

[0055] 10. Crankshaft; 11. Eccentric part; 12. Shaft body section;

[0056] 20. Cylinder liner; 21. Compression intake port; 22. Exhaust port; 23. Intake chamber; 24. Intake connecting chamber; 25. Exhaust chamber; 26. Connecting hole;

[0057] 30. Cross-groove structure; 31. Limiting channel; 311. Variable volume cavity; 32. Central hole;

[0058] 40. Slider; 41. Through hole; 42. Extrusion surface;

[0059] 50. Flange; 52. Upper flange; 53. Lower flange;

[0060] 60. Exhaust valve assembly;

[0061] 70. Exhaust cover;

[0062] 80. Dispenser assembly; 81. Housing assembly; 82. Motor assembly; 83. Pump body assembly; 84. Top cover assembly; 85. Bottom cover assembly;

[0063] 90. Fasteners. Detailed Implementation

[0064] 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.

[0065] In existing technologies, such as Figure 22 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.

[0066] 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.

[0067] 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 23 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.

[0068] 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.

[0069] However, as Figure 24 As 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 O1 and O0 and the sliding direction of the slider in the limiting groove.

[0070] like Figure 25 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.

[0071] Based on this, this application proposes a novel mechanism principle of a cross-slot structure 30 with two limiting channels 31 and two sliders 40, 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 30 with two limiting channels 31 and two sliders 40.

[0072] To address the issues of low energy efficiency and high noise levels in existing compressors, and how to ensure optimal overall compressor efficiency, this invention provides a fluid machine and a heat exchange device, wherein the heat exchange device includes a fluid machine, which is the fluid machine described above and below.

[0073] 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 the two eccentric portions 11, 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 arranged sequentially 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. There is a phase difference of a second included angle B between the extension directions of 31, wherein the first included angle A is twice the second included angle B; the slider 40 has a through hole 41, there are two sliders 40, and 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 311. The variable volume cavity 311 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.

[0074] 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 311. 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, i.e., the driving torque of the eccentric portion 11 corresponding to the slider 40 at the dead position... When the value is 0, the slider 40 at the dead point position 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 normally drive the corresponding slider 40 to rotate. This slider 40 drives the cross groove structure 30 to rotate, and then the cross groove structure 30 drives the slider 40 at the dead point position to continue to rotate. 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.

[0075] 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.

[0076] It should be noted that in this application, neither the first included angle A nor the second included angle B is zero.

[0077] like Figure 20 and Figure 21 As 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.

[0078] 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 20 ).

[0079] like Figure 20 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.

[0080] like Figure 21As 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.

[0081] 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.

[0082] 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.

[0083] It should be noted that, in this application, the maximum lever arm of the driving torque of the eccentric part 11 is 2e.

[0084] 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.

[0085] 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.

[0086] like Figures 1 to 19 As 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.

[0087] Specifically, such as Figure 6 As shown, the eccentricity of both eccentric parts 11 is equal to e, as... Figure 12 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 11 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.

[0088] 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.

[0089] Preferably, the range of the first assembly gap is 0.01 to 0.03 mm.

[0090] 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.

[0091] like Figure 2 , Figure 3 , Figure 6 , Figure 9 and Figure 12As 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.

[0092] 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.

[0093] Optionally, the first and second sections can be detachably connected. This ensures ease of assembly and disassembly of the crankshaft 10.

[0094] like Figure 2 , Figure 3 , Figure 6 , Figure 9 and Figure 12 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.

[0095] 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.

[0096] like Figure 3 and Figure 5 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.

[0097] 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.

[0098] Preferably, the first included angle A is 160 degrees and the second included angle B is 80 degrees.

[0099] Preferably, the first included angle A is 165 degrees and the second included angle B is 82.5 degrees.

[0100] Preferably, the first included angle A is 170 degrees and the second included angle B is 85 degrees.

[0101] Preferably, the first included angle A is 175 degrees and the second included angle B is 87.5 degrees.

[0102] Preferably, the first included angle A is 180 degrees and the second included angle B is 90 degrees.

[0103] Preferably, the first included angle A is 185 degrees and the second included angle B is 92.5 degrees.

[0104] Preferably, the first included angle A is 190 degrees and the second included angle B is 95 degrees.

[0105] Preferably, the first included angle A is 195 degrees and the second included angle B is 97.5 degrees.

[0106] 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.

[0107] like Figure 2 , Figure 3 , Figure 6 , Figure 9 and Figure 12 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.

[0108] like Figure 3 , Figure 5 , Figure 8 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.

[0109] 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.

[0110] like Figure 13 As 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 311. 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.

[0111] 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 13 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 13 The dashed X-line in the diagram represents the circle containing the center of the two arc surfaces.

[0112] Optionally, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner 20.

[0113] 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.

[0114] Preferably, the difference ranges from -0.02 to 0.02 mm.

[0115] 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.

[0116] Preferably, S 滑块 / S 排 The value is 12 to 18.

[0117] It should be noted that the fluid machinery shown in this embodiment is a compressor, such as... Figure 1 As 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.

[0118] Alternatively, the above-mentioned components can be connected by welding, heat fitting, or cold pressing.

[0119] 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 .

[0120] 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 311. The pump body assembly 83 has a total of 4 variable volume chambers 311. During the rotation of the crankshaft 10, the crankshaft 10 rotates 2 times, and a single variable volume chamber 311 completes 1 intake and exhaust process. For the compressor, the crankshaft 10 rotates 2 times, and a total of 4 intake and exhaust processes are completed.

[0121] 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 311.

[0122] like Figures 14 to 19 As shown, during the reciprocating motion of the slider 40 within the limiting channel 31, it simultaneously rotates relative to the cylinder liner 20. Figures 14 to 16 During the clockwise rotation of slider 40 from 0 degrees to 180 degrees, the variable volume cavity 311 increases in size. As the variable volume cavity 311 increases, it connects with the intake cavity 23 of cylinder liner 20. When slider 40 rotates to 180 degrees, the volume of the variable volume cavity 311 reaches its maximum value, at which point it disengages from the intake cavity 23, thus completing the intake operation. Figures 17 to 19 During the process of slider 40 continuing to rotate clockwise from 180 degrees to 360 degrees, the variable volume chamber 311 decreases, and slider 40 compresses the gas in the variable volume chamber 311. When slider 40 rotates to the point where the variable volume chamber 311 is connected to the compression exhaust port 22, and when the gas in the variable volume chamber 311 reaches the exhaust pressure, the exhaust valve plate of exhaust valve assembly 60 opens to start the exhaust operation until the compression is completed and the next cycle begins.

[0123] like Figures 14 to 19 As shown, the point marked M is used as the reference point for the relative motion between slider 40 and crankshaft 10. Figure 15 This represents the process of slider 40 rotating clockwise from 0 degrees to 180 degrees. The angle of rotation of slider 40 is θ1, and the corresponding angle of rotation of crankshaft 10 is 2θ1. Figure 17 The diagram shows the process of slider 40 continuing to rotate clockwise from 180 degrees to 360 degrees. The rotation angle of slider 40 is 180° + θ2, and the corresponding rotation angle of crankshaft 10 is 360° + 2θ2. Figure 18The diagram shows the process of slider 40 continuing to rotate clockwise from 180 degrees to 360 degrees, and the variable volume cavity 311 is connected to the compression exhaust port 22. The angle of rotation of slider 40 is 180°+θ3, and the corresponding angle of rotation of crankshaft 10 is 360°+2θ3. That is, when slider 40 rotates 1 revolution, the corresponding crankshaft 10 rotates 2 revolutions, where θ1 < θ2 < θ3.

[0124] Specifically, such as Figures 14 to 19 As shown, the cylinder liner 20 has a compression intake port 21 and a compression exhaust port 22. When any slider 40 is in the intake position, the compression intake port 21 is connected to the corresponding variable volume chamber 311; when any slider 40 is in the exhaust position, the corresponding variable volume chamber 311 is connected to the compression exhaust port 22.

[0125] like Figures 14 to 19 As shown, the inner wall of the cylinder liner 20 has an intake chamber 23, which is connected to the compression inlet 21. This ensures that the intake chamber 23 can store a large amount of gas, so that the variable volume chamber 311 can be fully saturated with gas, thereby enabling the compressor to draw in sufficient gas. When the intake is insufficient, the stored gas can be supplied to the variable volume chamber 311 in a timely manner to ensure the compression efficiency of the compressor.

[0126] 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.

[0127] 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.

[0128] like Figure 10 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. The compression inlet 21 is connected to the intake chambers 23 through the intake connecting chamber 24. This increases the volume of the intake chambers 23, thereby reducing intake pressure pulsation.

[0129] like Figure 2 As shown, the intake communication cavity 24 extends a second predetermined 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. 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.

[0130] like Figure 10 , Figures 14 to 19As shown, an exhaust chamber 25 is formed on the outer wall of the cylinder liner 20, and a compression exhaust port 22 is connected to the exhaust chamber 25 from the inner wall of the cylinder liner 20. The fluid machinery also includes an exhaust valve assembly 60, which is disposed in the exhaust chamber 25 and corresponding to the compression exhaust port 22. In this way, the exhaust chamber 25 is used to accommodate the exhaust valve assembly, which effectively reduces the space occupied by the exhaust valve assembly, makes the components more rationally arranged, and improves the space utilization of the cylinder liner 20.

[0131] like Figure 10 , Figures 14 to 19 As shown, there are two compression exhaust ports 22, which are spaced apart along the axial direction of the cylinder liner 20. There are two sets of exhaust valve assemblies, each corresponding to one of the two compression exhaust ports 22. In this way, since each of the two compression exhaust ports 22 is equipped with a separate set of exhaust valve assemblies, a large amount of gas leakage in the variable volume chamber 311 is effectively avoided, thus ensuring the compression efficiency of the variable volume chamber 311.

[0132] It should be noted that in this application, the exhaust valve assembly is connected to the cylinder liner 20 via fastener 90. The exhaust valve assembly includes an exhaust valve plate and a valve plate baffle. The exhaust valve plate is disposed within the exhaust chamber 25 and blocks the corresponding compressed exhaust port 22. The valve plate baffle overlaps and is disposed on the exhaust valve plate. In this way, the valve plate baffle effectively prevents the exhaust valve plate from over-opening, thereby ensuring the exhaust performance of the cylinder liner 20.

[0133] Optionally, fastener 90 is a screw.

[0134] like Figure 10 , Figure 13 , Figures 18 to 20 As shown, a connecting hole is also provided on the axial end face of the cylinder liner 20, which communicates with the exhaust chamber 25. The fluid machinery also includes a flange 50, on which an exhaust passage is provided, and the connecting hole communicates with the exhaust passage. This ensures the reliability of the exhaust of the cylinder liner 20.

[0135] like Figure 20 As shown, the exhaust chamber 25 extends to the outer wall of the cylinder liner 20. The fluid machinery also includes an exhaust cover plate 70, which is connected to the cylinder liner 20 and seals the exhaust chamber 25. In this way, the exhaust cover plate 70 serves to separate the variable volume chamber 311 from the external space of the pump body assembly 83.

[0136] like Figure 18 and Figure 19 As shown, when the variable volume chamber 311 is connected to the compression exhaust port 22, when the pressure of the variable volume chamber 311 reaches the exhaust pressure, the exhaust valve plate opens, and the compressed gas enters the exhaust chamber 25 through the compression exhaust port 22, passes through the connecting hole on the cylinder liner 20, and is then discharged through the exhaust passage and enters the external space of the pump body assembly 83 (i.e., the compressor cavity), thereby completing the exhaust process.

[0137] Optionally, the exhaust cover 70 is secured to the cylinder liner 20 by fasteners 90.

[0138] Optionally, fastener 90 is a screw.

[0139] Optionally, the outer contour of the exhaust cover 70 is adapted to the outer contour of the exhaust chamber 25.

[0140] The following is a detailed introduction to the operation of the compressor:

[0141] like Figure 1 As 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.

[0142] Other applications: By switching the positions of the intake and exhaust ports, this compressor can be used as an expander. That is, the compressor's exhaust port is used as the expander's intake port, high-pressure gas is introduced, and other driving mechanisms rotate. After expansion, the gas is discharged through the compressor's intake port (expander's exhaust port).

[0143] When the fluid machinery 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 connected to the corresponding variable volume chamber 311; when any slider 40 is in the exhaust position, the corresponding variable volume chamber 311 is connected to the expansion intake port. Thus, when high-pressure gas enters the variable volume chamber 311 through the expansion intake port, the high-pressure gas drives the cross-groove structure 30 to rotate. The rotation of the cross-groove structure 30 drives the slider 40 to rotate, and simultaneously causes the slider 40 to slide linearly relative to the cross-groove structure 30. This causes the slider 40 to drive the eccentric part 11 to rotate, that is, to drive the crankshaft 10 to rotate. By connecting this crankshaft 10 to other power-consuming devices, the crankshaft 10 can output power.

[0144] Optionally, the inner wall surface of the cylinder liner 20 has an expansion exhaust chamber, which is connected to the expansion exhaust port.

[0145] Furthermore, the expansion exhaust chamber extends circumferentially around the inner wall of the cylinder liner 20 by a first predetermined distance to form an arc-shaped expansion exhaust chamber, and the expansion exhaust chamber extends from the expansion exhaust port to the side where the expansion intake port is located, and the extension direction of the expansion exhaust chamber is in the same direction as the rotation direction of the cross groove structure 30.

[0146] Furthermore, there are two expansion exhaust chambers, which are spaced apart along the axial direction of the cylinder liner 20. The cylinder liner 20 also has an expansion exhaust communication chamber, and both expansion exhaust chambers are connected to the expansion exhaust communication chamber. The expansion exhaust port is connected to the expansion exhaust chamber through the expansion exhaust communication chamber.

[0147] Furthermore, the expansion exhaust communication cavity extends a second predetermined distance along the axial direction of the cylinder liner 20, and at least one end of the expansion exhaust communication cavity penetrates the axial end face of the cylinder liner 20.

[0148] To address the issue of ensuring optimal overall compressor efficiency, the first radial clearance C1 between the outer peripheral surface of the cross-groove structure 30 and the inner wall surface of the cylinder liner 20 has been reasonably optimized, as follows:

[0149] In this invention, the cross groove structure 30 is coaxially arranged with the cylinder liner 20, and there is a first radial gap C1 between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder liner 20. The range of the first radial gap C1 is 0.01 to 0.08 mm.

[0150] By applying the technical solution of this invention, based on the principle of optimal overall efficiency of the compressor, the radial dimension relationship of the pump body assembly of the compressor is clarified, and the scheme is optimized for each design variable that affects the radial dimension, thereby ensuring that the mechanical efficiency and volumetric efficiency of the compressor are both within a better range, and thus ensuring the optimal overall energy efficiency of the compressor.

[0151] Furthermore, considering that during compressor operation, the first radial gap C1 between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder liner 20 will be filled with lubricating oil, the lubrication between the cross groove structure 30 and the cylinder liner 20 will be hydrodynamic lubrication. Under hydrodynamic lubrication, the larger the gap, the greater the frictional power consumption, and the higher the mechanical efficiency of the compressor. At the same time, during compressor operation, there is a pressure difference between the gas at the ends of the slider 40 on both sides of its sliding direction. The side connected to the suction channel is the suction pressure, and the other end is the intermediate pressure or exhaust pressure during the compression process. The gas leaks from the high-pressure side to the low-pressure side through the first radial gap C1 between the cross groove structure 30 and the cylinder liner 20. The smaller the gap on the low-pressure side, the better the sealing, the smaller the leakage, and the higher the volumetric efficiency of the compressor.

[0152] In summary, the first radial clearance C1 has opposite effects on mechanical efficiency and volumetric efficiency. Through theoretical analysis and experimental verification, optimizing the range of the first radial clearance C1 to be within the range of 0.01 to 0.08 mm can improve the overall efficiency of the compressor.

[0153] Table 1. Effects of the first radial clearance C1 on various compressor efficiencies.

[0154]

[0155] Through Table 1 and in conjunction with Figure 26 It can be seen that the compressor's overall efficiency is optimal when the first radial clearance C1 is in the range of 0.015 to 0.03 mm.

[0156] It should be noted that during the assembly of the pump body assembly 83, the eccentric portion 11 of the crankshaft 10 needs to pass through the central hole 32. Simultaneously, considering that a larger diameter of the eccentric portion 11 results in a larger outer diameter of the cross-groove structure 30, leading to higher overall mechanical power consumption, the diameter of the central hole 32 is larger than the diameter of the eccentric portion 11. A second radial clearance C2 exists between the hole wall of the central hole 32 and the outer circumferential surface of the eccentric portion 11. (Refer to Table 2 and...) Figure 27 It is known that when the second radial clearance C2 is in the range of 0.05 to 1 mm, the mechanical efficiency of the compressor is relatively high. Thus, by reasonably optimizing the second radial clearance C2 between the hole wall of the central hole 32 and the outer peripheral surface of the eccentric part 11, the second radial clearance C2 is made as small as possible while ensuring that the eccentric part 11 can pass smoothly through the central hole 32.

[0157] Table 2. Effect of the second radial clearance C2 on the mechanical efficiency of the compressor.

[0158]

[0159] like Figure 4 and Figure 5 As shown, the inner diameter D of cylinder liner 20 缸套 With the outer diameter d of the cross groove structure 30 槽 The following conditions must be met: D 缸套 =d 槽 +2C1; Diameter D of center hole 32 限 The diameter d of the eccentric part 11 偏 The following conditions must be met: D 限 =d 偏 +2C2.

[0160] It should be noted that during the operation of the compressor, the inner cavity of the cross groove structure 30 is under high pressure. During the suction stage, the pressure in the variable volume chamber 311 is the suction pressure, which is under low pressure. During the compression process, the pressure in the variable volume chamber 311 gradually increases and is in an intermediate pressure state that is greater than the suction pressure and less than the discharge pressure. After reaching the discharge pressure, the compressor enters the discharge stage. During the discharge process, the pressure in the variable volume chamber 311 remains constant at the discharge pressure (high pressure).

[0161] like Figure 3 , Figure 8 and Figure 9As shown, the slider 40 has a pressing surface 42 facing the end of the limiting channel 31. The pressing surface 42 serves as the head of the slider 40 and faces the variable volume cavity 311. The pressing surface 42 is an arc surface, and there is a sealing distance M between the top of the arc surface and the hole wall of the central hole 32. The sealing distance M changes periodically as the slider 40 slides in the limiting channel 31.

[0162] Furthermore, during the intake and compression processes, the pressure inside the cross groove structure 30 is higher than the pressure inside the variable volume chamber 311. Under the influence of the pressure difference, there will be a certain amount of leakage. The size of the leakage is inversely proportional to the sealing distance M, that is, the larger the sealing distance M is, the smaller the leakage.

[0163] Specifically, when the pump body assembly 83 is at 180° (i.e., the suction is finished), the sealing distance M is the smallest, and the pressure difference on both sides of the leakage channel is the largest at this position, and the leakage is also the largest. The larger the sealing distance M is, the larger the outer diameter of the cross groove structure 30 is, and the greater the frictional power consumption of the compressor. It can be seen that the sealing distance M has opposite effects on the volumetric efficiency and mechanical efficiency of the compressor, and there is an optimal range.

[0164] Furthermore, the sealing distance M has a minimum sealing distance M 最小 Minimum sealing distance M 最小 The range is 1 to 6 mm.

[0165] Table 3 Minimum Sealing Distance M 最小 Impact on various efficiencies of the compressor

[0166] <![CDATA[Minimum sealing distance M 最小 > 1mm 2mm 3mm 4mm 5mm 6mm mechanical efficiency 93.3％ 92.7％ 91.8％ 90.0％ 88.2％ 85.3％ Volumetric efficiency 88.5％ 91.3％ 91.5％ 91.7％ 92.2％ 93.2％ Overall efficiency 82.6％ 84.6％ 84.0％ 82.5％ 81.3％ 79.5％

[0167] Furthermore, combining Table 3 and Figure 28 It can be seen that the minimum sealing distance M 最小 When the thickness is within the range of 2 to 4 mm, the overall efficiency of the compressor is relatively high.

[0168] It should be noted that, in this application, the sealing distance M has a minimum sealing distance M 最小 The outer diameter d of the cross groove structure 30 槽 The diameter D of the center hole 32 限 The eccentricity e of eccentric part 11 satisfies the following condition: 槽 =D 限 +8e+2M 最小 .

[0169] like Figure 6 and Figure 7 As shown, the eccentric part 11 is cylindrical, and the proximal end of the eccentric part 11 protrudes from the outer circle of the shaft body portion of the crankshaft 10.

[0170] It should be noted that during the assembly of the pump body assembly 83, the shaft portion 12 of the crankshaft 10 first passes through the through hole 41 of the slider 40, and then the eccentric portion 11 of the crankshaft 10 passes through the through hole 41. During this process, any position of the outer circle of the eccentric portion 11 of the crankshaft 10 needs to protrude from the outer circle of the shaft portion 12. That is, the protrusion T of the proximal end of the eccentric portion 11 must satisfy: T > 0. Otherwise, normal assembly cannot be completed. The position with the minimum protrusion T is when the proximal end of the eccentric portion 11 protrudes from the outer circle of the shaft portion 12 of the crankshaft 10.

[0171] Table 4. Effect of minimum protrusion T on the mechanical efficiency of the compressor.

[0172]

[0173] Preferably, in conjunction with Table 4 and Figure 29 It can be seen that when the protrusion T of the eccentric part 11 near the proximal end is in the range of 0.1 to 2 mm, the mechanical efficiency of the compressor is relatively high.

[0174] like Figure 6 and Figure 7 As shown, d 偏 / 2=e+d 轴 / 2+T, where d 偏 d is the diameter of the eccentric part 11. 轴 denoted as , e as eccentricity of eccentric portion 11, and T as protrusion of the proximal end of eccentric portion 11.

[0175] Furthermore, the protrusion T at the proximal end of the eccentric portion 11 and the diameter d of the eccentric portion 11 are... 偏 The diameter d of the shaft section 轴 The eccentricity e of eccentric part 11 satisfies the following condition: 偏 =d 轴 +2e+2T.

[0176] 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.

[0177] 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.

[0178] 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.

[0179] 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.

[0180] 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.

[0181] 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 by, The fluid machine comprises: a crankshaft (10) provided with two eccentric portions (11) along the axial direction thereof; a cylinder sleeve (20) eccentrically arranged with the crankshaft (10) and fixed in eccentric distance; a cross-groove structure (30) rotatably arranged in the cylinder sleeve (20) and coaxially arranged with the cylinder sleeve (20), wherein a first radial gap C1 is formed between the outer circumferential surface of the cross-groove structure (30) and the inner wall surface of the cylinder sleeve (20), and the first radial gap C1 ranges from 0.015 mm to 0.03 mm; the cross-groove structure (30) is provided with two limiting channels (31) 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); two sliders (40) provided with through holes (41), wherein the two eccentric portions (11) correspondingly extend into the two through holes (41) of the two sliders (40), and the two sliders (40) are correspondingly arranged in the two limiting channels (31) and form a variable volume cavity (311) in the sliding direction of the sliders (40); when the crankshaft (10) rotates to drive the sliders (40) to reciprocally slide in the limiting channels (31) and interact with the cross-groove structure (30), the cross-groove structure (30) and the sliders (40) rotate in the cylinder sleeve (20).

2. The fluid machine of claim 1, wherein, The cross-groove structure (30) is provided with a central hole (32) through which the two limiting channels (31) are communicated, and the hole diameter of the central hole (32) is greater than the diameter of the shaft portion (12) of the crankshaft (10).

3. The fluid machine of claim 2, wherein, The hole diameter of the central hole (32) is greater than the diameter of the eccentric portion (11), and a second radial gap C2 is formed between the hole wall surface of the central hole (32) and the outer circumferential surface of the eccentric portion (11), and the second radial gap C2 ranges from 0.05 mm to 1 mm.

4. The fluid machine according to claim 3, wherein The inner circle diameter D of the cylinder liner (20) 缸套 The outer circle diameter d of the cross groove structure (30) 槽 D 缸套 =d 槽 +2C1 The diameter D of the central hole (32) 限 The diameter d of the eccentric part (11) 偏 The following conditions must be met: D 限 =d 偏 +2C2.

5. The fluid machine according to claim 2, wherein The slider (40) is provided with a pressing surface (42) facing the end of the limiting channel (31), the pressing surface (42) serving as the head of the slider (40), and the pressing surface (42) faces the variable volume cavity (311). The pressing surface (42) is an arc surface, a top end of the arc surface and the hole wall surface of the central hole (32) form a sealing distance M, and the sealing distance M periodically changes with the sliding of the slider (40) in the limiting channel (31).

6. The fluid machine of claim 5, wherein, The sealing distance M has a minimum sealing distance M 最小 The minimum sealing distance M 最小 The range is 1~6mm.

7. The fluid machine of claim 6, wherein, The minimum sealing distance M 最小 is in the range of 2 to 4 mm.

8. The fluid machine of claim 5, wherein, The sealing distance M has a minimum sealing distance M 最小 The outer circle diameter d of the cross groove structure (30) 槽 The hole diameter D of the center hole (32) 限 The eccentric amount e of the eccentric portion (11) satisfies: d 槽 = D 限 + 8e + 2M 最小 .

9. The fluid machine of claim 1, wherein, The eccentric portion (11) is a cylindrical shape, and the proximal end of the eccentric portion (11) protrudes from the outer circle of the shaft portion (12) of the crankshaft (10).

10. The fluid machine of claim 9, wherein, The protrusion amount T of the proximal end of the eccentric portion (11) satisfies T>0.

11. The fluid machine of claim 10, wherein, The protruding amount T of the proximal end of the eccentric part (11) ranges from 0.1 to 2 mm.

12. The fluid machine of claim 9, wherein, The protrusion T of the proximal end of the eccentric portion (11), the diameter d of the eccentric portion (11) 偏 , the diameter d of the shaft body portion (12) 轴 , and the eccentricity e of the eccentric portion (11) satisfy the following relationship: d 偏 = d 轴 + 2e + 2T.

13. The fluid machine of any one of claims 1 to 12, wherein, The two eccentric parts (11) have a phase difference of a first included angle A, the eccentric amounts of the two eccentric parts (11) are equal, and the extension directions of the two limiting 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.

14. A heat exchange apparatus comprising a fluid machine, characterized by The fluid machine is the fluid machine according to any one of claims 1 to 13.

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