Fluid machine and heat exchange device with bearing

Abstract

This invention provides a fluid machine and heat exchange device with bearings. The fluid machine with bearings includes a crankshaft, a cylinder liner, bearings, a cross-groove structure, and sliders. The crankshaft has two eccentric portions; the crankshaft and cylinder liner are eccentrically arranged with a fixed eccentric distance; there is at least one bearing, which is located inside the cylinder liner at the axial end of the cylinder liner, and the outer ring of the bearing is in contact with the inner wall of the cylinder liner; the cross-groove structure is rotatably arranged inside the cylinder liner, and the outer circumferential surface of the cross-groove structure is in contact with the inner ring of the bearing; two limiting channels of the cross-groove structure are sequentially arranged along the axial direction of the crankshaft, and the extension direction of the limiting channels is perpendicular to the axial direction of the crankshaft; the sliders have through holes, and there are two sliders. The two eccentric portions extend into the two through holes of the two sliders respectively, and the two sliders are slidably arranged in the two limiting channels to form a variable volume cavity. This invention solves the problems of low energy efficiency and high noise in existing compressors.

Description

Technical Field

[0001] This invention relates to the field of heat exchange system technology, and more specifically, to a fluid machine and heat exchange device with bearings. 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. Scroll compressors, as the mainstream type of household air conditioner compressor, have matured after nearly a century of development, but their structural principles limit their potential for optimization. Significant breakthroughs require innovation in their structural principles.

[0004] Therefore, there is an urgent need to develop a compressor with high energy efficiency and low noise. Summary of the Invention

[0005] The main objective of this invention is to provide a fluid machinery and heat exchange device with bearings to solve the problems of low energy efficiency and high noise in existing compressors.

[0006] To achieve the above objectives, according to one aspect of the present invention, a fluid machine with bearings is provided, comprising a crankshaft, a cylinder liner, bearings, 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; there is at least one bearing, which is disposed within the cylinder liner and located at the axial end of the cylinder liner, with the outer ring of the bearing fitting against the inner wall of the cylinder liner; the cross-groove structure is rotatably disposed within the cylinder liner, with its outer peripheral surface fitting against the inner ring of the bearing, and the cross-groove structure has two limiting channels, which are sequentially arranged along the axial direction of the crankshaft, with the extension 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, and the two sliders correspondingly sliding within the two limiting channels to form a variable volume cavity, the variable volume cavity being located in the sliding direction of the sliders; 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.

[0007] Furthermore, an annular groove is provided on the axial end face of the cylinder liner. The distance by which the bottom of the annular groove extends radially inward along the cylinder liner is equal to the distance between the inner and outer rings of the bearing. The bearing is installed in the annular groove.

[0008] Furthermore, a bearing is provided at only one end of the axial end of the cylinder liner; or, bearings are provided at both ends of the axial end of the cylinder liner.

[0009] Furthermore, the diameter Q of the outer circumference of the cross-groove structure and the height N of the bearing satisfy the following relationship: 3≤Q / N≤7.

[0010] 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.

[0011] Furthermore, the eccentricity of the eccentric part is equal to the assembly eccentricity of the crankshaft and cylinder liner.

[0012] Furthermore, both ends of the limiting channel extend to the outer periphery of the cross groove structure.

[0013] Furthermore, the two sliders are respectively concentrically set with the two eccentric parts, and the sliders move in a circular motion around the eccentric parts. There is a first rotational gap between the hole wall and the eccentric part, and the range of the first rotational gap is 0.005mm to 0.05mm.

[0014] Furthermore, the cross groove structure is coaxially arranged with the cylinder liner, and there is a second rotational clearance between the outer peripheral surface of the cross groove structure and the inner wall surface of the cylinder liner. The range of the second rotational clearance is 0.005mm to 0.08mm.

[0015] Furthermore, the first included angle A is 160 degrees to 200 degrees; the second included angle B is 80 degrees to 100 degrees.

[0016] Furthermore, the fluid machinery also includes a flange, which is located at the axial end of the cylinder liner, and the crankshaft is concentrically positioned with the flange.

[0017] Furthermore, there is a first assembly clearance between the crankshaft and the flange, the first assembly clearance being in the range of 0.005mm to 0.05mm.

[0018] Furthermore, the range of the first assembly gap is 0.01 to 0.03 mm.

[0019] Furthermore, the eccentric part has a circular arc surface with a central angle greater than or equal to 180 degrees.

[0020] Furthermore, the eccentric part is cylindrical.

[0021] Furthermore, the proximal end of the eccentric portion is flush with the outer circle of the crankshaft body portion; or, the proximal end of the eccentric portion protrudes beyond the outer circle of the crankshaft body portion; or, the proximal end of the eccentric portion is located inside the outer circle of the crankshaft body portion.

[0022] Furthermore, the slider comprises multiple substructures, which are spliced ​​together to form a through hole.

[0023] Furthermore, the two eccentric parts are spaced apart axially on the crankshaft.

[0024] 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.

[0025] Furthermore, the diameter of the central hole is larger than the diameter of the eccentric part.

[0026] 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.

[0027] Furthermore, the slider has a pressing surface facing the end of the limiting channel, which serves as the head of the slider and faces the variable volume cavity.

[0028] Furthermore, the extrusion surface is an arc surface, and the distance between the center of the arc surface and the center of the through hole is equal to the eccentricity of the eccentric part.

[0029] Furthermore, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner; or, the radius of curvature of the arc surface has a difference from the radius of the inner circle of the cylinder liner, the difference being in the range of -0.05mm to 0.025mm.

[0030] Furthermore, the difference ranges from -0.02 to 0.02 mm.

[0031] Furthermore, the projected area S of the extrusion surface in the sliding direction of the slider 滑块 The area of ​​the compression exhaust port of the cylinder liner is S 排 The following conditions must be met between them: S 滑块 / S 排 The value is 8 to 25.

[0032] Furthermore, S 滑块 / S 排 The value is 12 to 18.

[0033] Furthermore, the diameter R of the outer circumference of the cross groove structure and the height N of the bearing satisfy the following condition: 1.5≤R / N≤3.5.

[0034] Furthermore, the cylinder liner has a compression intake port and a compression exhaust port. When any slider is in the intake position, the compression intake port is connected to the corresponding variable volume chamber; when any slider is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port.

[0035] Furthermore, the inner wall of the cylinder liner has an intake chamber, which is connected to the compression intake port.

[0036] 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.

[0037] 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 connecting chamber, and both intake chambers are connected to the intake connecting chamber. The compression intake port is connected to the intake chamber through the intake connecting chamber.

[0038] Furthermore, the intake communication chamber extends a second preset distance along the axial direction of the cylinder liner.

[0039] Furthermore, there are two intake chambers, which are spaced apart along the axial direction of the cylinder liner. There are also two compression inlets, which are arranged in a one-to-one correspondence with and connected to the two intake chambers.

[0040] Furthermore, an exhaust chamber is provided on the outer wall of the cylinder liner, and a compressed exhaust port is connected to the exhaust chamber from the inner wall of the cylinder liner. The fluid machinery also includes an exhaust valve assembly, which is disposed in the exhaust chamber and corresponding to the compressed exhaust port.

[0041] Furthermore, there are two compression exhaust ports, which are spaced apart along the axial direction of the cylinder liner. There are two sets of exhaust valve assemblies, which are respectively set to correspond to the two compression exhaust ports.

[0042] Furthermore, a connecting hole is provided on the axial end face of the cylinder liner, which communicates with the exhaust chamber. The fluid machinery also includes a flange, on which an exhaust passage is provided, and the connecting hole communicates with the exhaust passage.

[0043] Furthermore, the exhaust chamber extends to the outer wall of the cylinder liner, and the fluid machinery also includes an exhaust cover plate, which is connected to the cylinder liner and seals the exhaust chamber.

[0044] Furthermore, fluid machinery is the compressor.

[0045] Furthermore, the cylinder liner has an expansion exhaust port and an expansion intake port. When any slider is in the intake position, the expansion exhaust port is connected to the corresponding variable volume chamber; when any slider is in the exhaust position, the corresponding variable volume chamber is connected to the expansion intake port.

[0046] Furthermore, the inner wall surface of the cylinder liner has an expansion exhaust chamber, which is connected to the expansion exhaust port.

[0047] Furthermore, the expansion exhaust chamber extends circumferentially around the inner wall of the cylinder 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, with the extension direction of the expansion exhaust chamber being in the same direction as the rotation direction of the cross groove structure.

[0048] Furthermore, there are two expansion exhaust chambers, which are spaced apart along the axial direction of the cylinder liner. The cylinder liner 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.

[0049] Furthermore, the expansion exhaust communication cavity extends a second predetermined distance along the axial direction of the cylinder liner, and at least one end of the expansion exhaust communication cavity penetrates the axial end face of the cylinder liner.

[0050] Furthermore, fluid machinery is an expander.

[0051] 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.

[0052] By applying the technical solution of this invention, the cross-groove structure is configured with two limiting channels and two corresponding sliders. The two eccentric parts of the crankshaft extend into the two through holes of the two sliders. Simultaneously, the two sliders are slidably disposed within the two limiting channels to form a variable volume cavity. Thus, when one of the two sliders is at a dead point position, i.e., the driving torque of the eccentric part corresponding to the slider at the dead point position is 0, the slider at the dead point position cannot continue to rotate. At this time, the driving torque of the other eccentric part driving the corresponding slider is at its maximum value, ensuring that the eccentric part with the maximum driving torque can normally drive the corresponding slider to rotate. This slider drives the cross-groove structure to rotate, and in turn, the cross-groove structure drives the slider at the dead point position to continue to rotate. This achieves stable operation of the fluid machinery, avoids the dead point position of the moving mechanism, improves the motion reliability of the fluid machinery, and ensures high energy efficiency and low noise of the compressor, thereby ensuring the working reliability of the heat exchange equipment.

[0053] Furthermore, by providing at least one bearing inside the cylinder liner and at its axial end, with the outer ring of the bearing fitting against the inner wall of the cylinder liner, the outer circumferential surface of the cross groove structure is supported and friction is reduced by the bearing. This changes the sliding friction between the circumferential outer surface of the cross groove structure and the inner wall of the cylinder liner to rolling friction between the circumferential outer surface of the cross groove structure and the bearing, thereby reducing mechanical friction power consumption. The inner ring of the bearing fits with the cross groove structure, and the inner ring of the bearing fits with the inner wall of the cylinder liner. Attached Figure Description

[0054] 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:

[0055] Figure 1 A schematic diagram illustrating the operating principle of a compressor according to an optional embodiment of the present invention is shown;

[0056] Figure 2 It shows Figure 1 A schematic diagram illustrating the operating principle of the compressor in the diagram;

[0057] Figure 3 A schematic diagram of the internal structure of a compressor according to Embodiment 1 of the present invention is shown;

[0058] Figure 4 It shows Figure 3 A schematic diagram of the pump body assembly of the compressor in the image;

[0059] Figure 5 It shows Figure 4 A schematic diagram of a pump body assembly in which bearings are present at both axial ends of the cross-groove structure.

[0060] Figure 6 It shows Figure 4 A schematic diagram of a bearing with an optional embodiment at both axial ends of the cross-groove structure;

[0061] Figure 7 It shows Figure 4 An exploded view of the pump body components;

[0062] Figure 8 It shows Figure 7 A schematic diagram of the assembly structure of the crankshaft, cross groove structure, and slider;

[0063] Figure 9 It shows Figure 8 A cross-sectional view of the crankshaft, cross groove structure, and slider in the diagram;

[0064] Figure 10 It shows Figure 7 A schematic diagram of the eccentricity of the crankshaft shaft body and the two eccentric parts.

[0065] Figure 11 It shows Figure 7 A cross-sectional structural schematic diagram of the assembly eccentricity of the crankshaft and cylinder liner;

[0066] Figure 12 It shows Figure 7 A schematic diagram of the cylinder liner and lower flange in a disassembled state;

[0067] Figure 13 It shows Figure 12 A structural schematic diagram of the eccentricity between the cylinder liner and the lower flange;

[0068] Figure 14 It shows Figure 7 A schematic diagram of the slider in the through hole along its axial direction;

[0069] Figure 15 It shows Figure 7 A schematic diagram of the cylinder liner structure;

[0070] Figure 16 It shows Figure 15 The diagram shows a cross-sectional view of the cylinder liner, in which the exhaust cover is omitted.

[0071] Figure 17 It shows Figure 16 A schematic diagram of the structure from the Y-axis perspective;

[0072] Figure 18 It shows Figure 4 A cross-sectional view of the cylinder liner and lower flange is shown in the figure, which illustrates the intake path of the pump body assembly.

[0073] Figure 19 It shows Figure 18 A schematic diagram of the cylinder liner structure;

[0074] Figure 20 It shows Figure 19 A cross-sectional view of the cylinder liner;

[0075] Figure 21 It shows Figure 19 A cross-sectional view of the cylinder liner from another perspective;

[0076] Figure 22 It shows Figure 4 A cross-sectional view of the pump body assembly from another perspective;

[0077] Figure 23 It shows Figure 22 A schematic diagram of the upper flange in the diagram;

[0078] Figure 24 It shows Figure 22 A schematic diagram of the lower flange in the diagram;

[0079] Figure 25 It shows Figure 3 A schematic diagram of the compressor in the intake state.

[0080] Figure 26 It shows Figure 3 A schematic diagram of the compressor in the intake process.

[0081] Figure 27 It shows Figure 3 A schematic diagram of the compressor in the state at the end of the intake phase;

[0082] Figure 28 It shows Figure 3A schematic diagram of the compressor's state when it is compressing gas;

[0083] Figure 29 It shows Figure 3 A schematic diagram of the compressor in the exhaust process.

[0084] Figure 30 It shows Figure 3 A schematic diagram of the compressor in the state at the end of exhaust;

[0085] Figure 31 It shows Figure 4 A schematic diagram of a bearing with an optional embodiment at both axial ends of the cross-groove structure;

[0086] Figure 32 A schematic diagram of the internal structure of a compressor according to Embodiment 2 of the present invention is shown;

[0087] Figure 33 It shows Figure 32 A schematic diagram of the pump body assembly of the compressor in the image;

[0088] Figure 34 A schematic diagram of the internal structure of a compressor according to Embodiment 3 of the present invention is shown;

[0089] Figure 35 It shows Figure 34 A schematic diagram of the pump body assembly of the compressor in the image;

[0090] Figure 36 A schematic diagram of a cross-groove structure and a slider according to an optional embodiment of the present invention is shown;

[0091] Figure 37 A schematic diagram of a cross-groove structure and a slider according to an optional embodiment of the present invention is shown;

[0092] Figure 38 A schematic diagram of a cross-groove structure and a slider according to an optional embodiment of the present invention is shown;

[0093] Figure 39 A schematic diagram of a cross-groove structure and a slider according to an optional embodiment of the present invention is shown;

[0094] Figure 40 A schematic diagram illustrating the operating principle of a compressor in the prior art is shown;

[0095] Figure 41 A schematic diagram illustrating the operating principle of the improved compressor in the prior art is shown;

[0096] Figure 42 It shows Figure 41The diagram shows the mechanism of the compressor in operation, which illustrates the lever arm that drives the slider to rotate.

[0097] Figure 43 It shows Figure 41 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.

[0098] The above figures include the following reference numerals:

[0099] 10. Crankshaft; 11. Eccentric part; 12. Shaft body section;

[0100] 20. Cylinder liner; 21. Compression intake port; 22. Compression exhaust port; 23. Intake chamber; 24. Intake connecting chamber; 25. Exhaust chamber; 26. Connecting hole; 210. Annular groove;

[0101] 30. Cross-groove structure; 31. Limiting channel; 311. Variable volume cavity; 32. Central hole;

[0102] 40. Slider; 41. Through hole; 42. Extrusion surface;

[0103] 50. Flange; 51. Venting channel; 52. Upper flange; 53. Lower flange;

[0104] 60. Exhaust valve assembly; 61. Exhaust valve plate; 62. Valve plate baffle;

[0105] 70. Exhaust cover;

[0106] 80. Dispenser assembly; 81. Housing assembly; 82. Motor assembly; 83. Pump body assembly; 84. Top cover assembly; 85. Bottom cover assembly;

[0107] 90. Fasteners;

[0108] 200. Bearings. Detailed Implementation

[0109] 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.

[0110] In existing technologies, such as Figure 40As 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.

[0111] 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.

[0112] 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 41 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.

[0113] 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.

[0114] However, as Figure 42 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 O1O0 and the sliding direction of the slider in the limiting groove.

[0115] like Figure 43 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.

[0116] 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.

[0117] To address the issues of low energy efficiency and high noise levels in existing compressors, this invention provides a fluid machinery and heat exchange device with bearings, wherein the heat exchange device includes the fluid machinery described below.

[0118] The fluid machinery with bearings of the present invention includes a crankshaft 10, a cylinder liner 20, a bearing 200, a cross-groove structure 30, and a slider 40. The crankshaft 10 has two eccentric portions 11 along its axial direction; the crankshaft 10 and the cylinder liner 20 are eccentrically positioned with a fixed eccentric distance; there is at least one bearing 200, which is disposed within the cylinder liner 20 and located at the axial end of the cylinder liner 20, with its outer ring fitting against the inner wall of the cylinder liner 20; the cross-groove structure 30 is rotatably disposed within the cylinder liner 20, with its outer peripheral surface fitting against the inner ring of the bearing 200, and the cross-groove structure 30 has two limiting channels 3. 1. Two limiting channels 31 are arranged sequentially along the axial direction of the crankshaft 10, and the extension direction of the limiting channels 31 is perpendicular to the axial direction of the crankshaft 10; 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 arranged 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.

[0119] By configuring the cross-groove structure 30 with two limiting channels 31 and correspondingly configuring 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. Thus, 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 is 0, the slider 40 at the dead position cannot continue to rotate, and at this time, the two eccentric portions 11... The other eccentric part 11 in 1 drives the corresponding slider 40 to the maximum driving torque, 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, which is 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, and improves the motion reliability of the fluid machinery. In other words, it ensures that the compressor has high energy efficiency and low noise, thereby ensuring the working reliability of the heat exchange equipment.

[0120] Furthermore, by providing at least one bearing 200 within the cylinder liner 20 and at its axial end, with the outer ring of the bearing 200 fitting against the inner wall of the cylinder liner 20, the outer circumferential surface of the cross groove structure 30 is supported and friction-reduced by the bearing 200. This transforms the sliding friction between the circumferential outer surface of the cross groove structure 30 and the inner wall of the cylinder liner 20 into rolling friction between the circumferential outer surface of the cross groove structure 30 and the bearing 200, thereby reducing mechanical friction power consumption. The inner ring of the bearing 200 mates with the cross groove structure 30, and the inner ring of the bearing 200 mates with the inner wall of the cylinder liner 20.

[0121] It should be noted that in this application, neither the first included angle A nor the second included angle B is zero.

[0122] like Figure 1 and Figure 2As 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.

[0123] 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 1 ).

[0124] like Figure 1 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.

[0125] like Figure 2 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.

[0126] Furthermore, the operating method also includes the same rotational angular velocity of the slider 40 relative to the eccentric part 11 as the same revolution angular velocity of the slider 40 around the axis O0 of the crankshaft 10; and the same revolution angular velocity of the cross groove structure 30 around the axis O0 of the crankshaft 10 as the same rotational angular velocity of the slider 40 relative to the eccentric part 11.

[0127] 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.

[0128] It should be noted that, in this application, the maximum lever arm of the driving torque of the eccentric part 11 is 2e.

[0129] 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.

[0130] 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.

[0131] The following three optional implementations will provide a detailed description of the structure of the fluid machinery, so as to better illustrate the operation method of the fluid machinery through its structural features.

[0132] Example 1

[0133] like Figures 3 to 31As shown, in this embodiment, both ends of the cylinder liner 20 have bearings 200. This ensures the smooth rotation of the cross-groove structure 30 within the cylinder liner 20.

[0134] like Figure 7 and Figure 19 As shown, an annular groove 210 is provided at the axial end face of the cylinder liner 20. The distance by which the bottom of the annular groove 210 extends radially inward along the cylinder liner 20 is equal to the distance between the inner and outer rings of the bearing 200. The bearing 200 is installed in the annular groove 210. In this way, the bearing 200 is installed in the cylinder liner 20 in an embedded manner, which can not only effectively prevent the cross groove structure 30 from tilting and reduce mechanical friction, but also keep the height of each component of the pump body assembly 83 constant, which is convenient for mass production.

[0135] like Figure 6 As shown, the diameter Q of the outer circumferential surface of the cross groove structure 30 and the height N of the bearing 200 satisfy the following relationship: 3 ≤ Q / N ≤ 7. The diameter R of the outer circumferential surface of the cross groove structure 30 and the height N of the bearing 200 satisfy the following relationship: 1.5 ≤ R / N ≤ 3.5. This effectively prevents the cross groove structure 30 from tilting, ensuring good lubrication between the cross groove structure 30 and the cylinder liner 20, thereby reducing the mechanical friction power consumption between the cross groove structure 30 and the cylinder liner 20, which is beneficial to improving compressor performance and thus enhancing the compressor's operational reliability.

[0136] like Figure 1 As shown, there is a phase difference of a first included angle A between the two eccentric parts 11, the eccentricity of the two eccentric parts 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.

[0137] like Figures 3 to 31 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.

[0138] Specifically, such as Figure 10 As shown, the eccentricity of both eccentric parts 11 is equal to e, as... Figure 11As 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 13 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.

[0139] like Figure 7 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.

[0140] like Figure 4 , Figures 7 to 11 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.

[0141] 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.

[0142] Optionally, the first and second sections can be detachably connected. This ensures ease of assembly and disassembly of the crankshaft 10.

[0143] like Figure 4 , Figures 7 to 11 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.

[0144] 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.

[0145] 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 eccentric parts 11. There is a first rotation gap between the hole wall of the through hole 41 and the eccentric part 11. The range of the first rotation gap is 0.005mm to 0.05mm.

[0146] Optionally, the cross groove structure 30 is coaxially arranged with the cylinder liner 20, and there is a second rotational clearance between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder liner 20, the second rotational clearance being in the range of 0.005mm to 0.08mm.

[0147] 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.

[0148] Preferably, the first included angle A is 160 degrees and the second included angle B is 80 degrees.

[0149] Preferably, the first included angle A is 165 degrees and the second included angle B is 82.5 degrees.

[0150] Preferably, the first included angle A is 170 degrees and the second included angle B is 85 degrees.

[0151] Preferably, the first included angle A is 175 degrees and the second included angle B is 87.5 degrees.

[0152] Preferably, the first included angle A is 180 degrees and the second included angle B is 90 degrees.

[0153] Preferably, the first included angle A is 185 degrees and the second included angle B is 92.5 degrees.

[0154] Preferably, the first included angle A is 190 degrees and the second included angle B is 95 degrees.

[0155] Preferably, the first included angle A is 195 degrees and the second included angle B is 97.5 degrees.

[0156] 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.

[0157] Preferably, the range of the first assembly gap is 0.01 to 0.03 mm.

[0158] 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.

[0159] like Figure 4 , Figures 7 to 11 As shown, the eccentric part 11 is cylindrical.

[0160] Optionally, the proximal end of the eccentric portion 11 is flush with the outer circle of the shaft portion 12 of the crankshaft 10.

[0161] Optionally, the proximal end of the eccentric portion 11 protrudes beyond the outer circle of the shaft portion 12 of the crankshaft 10.

[0162] Optionally, the proximal end of the eccentric portion 11 is located inside the outer circle of the shaft portion 12 of the crankshaft 10.

[0163] 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.

[0164] like Figure 4 , Figures 7 to 11 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.

[0165] like Figure 7 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.

[0166] 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.

[0167] like Figure 14 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.

[0168] 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 14 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 14 The dashed X-line in the diagram represents the circle containing the center of the two arc surfaces.

[0169] It should be noted that, in this application, if Figure 7 As 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.

[0170] Optionally, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner 20.

[0171] 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.

[0172] Preferably, the difference ranges from -0.02 to 0.02 mm.

[0173] 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 of ​​the compression exhaust port 22 of cylinder liner 20 is S 排 The following conditions must be met between them: S 滑块 / S 排 The value is 8 to 25.

[0174] Preferably, S 滑块 / S 排 The value is 12 to 18.

[0175] It should be noted that the fluid machinery shown in this embodiment is a compressor, such as... Figure 3 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.

[0176] Alternatively, the above-mentioned components can be connected by welding, heat fitting, or cold pressing.

[0177] 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 4 and Figure 5 .

[0178] 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.

[0179] like Figures 25 to 30 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 25 to 27 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 28 to 30 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 61 of the exhaust valve assembly 60 opens, and the exhaust operation begins until the compression is completed and the next cycle begins.

[0180] like Figures 25 to 30 As shown, the point marked M is used as the reference point for the relative motion between slider 40 and crankshaft 10. Figure 26 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 28 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 29 The 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.

[0181] Specifically, such as Figure 12 , Figures 15 to 21 , Figures 25 to 30As 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.

[0182] like Figure 12 , Figures 15 to 21 , Figures 25 to 30 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.

[0183] 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.

[0184] 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.

[0185] like Figure 15 , Figure 16 and Figure 18 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.

[0186] like Figure 15 , Figure 16 and Figure 18 As shown, the intake communication chamber 24 extends a second preset distance along the axial direction of the cylinder liner 20.

[0187] like Figures 19 to 21 As shown, another embodiment of the cylinder liner 20 is provided. There are two intake chambers 23, spaced apart along the axial direction of the cylinder liner 20. There are also two compression inlets 21, each corresponding to and connected to one of the two intake chambers 23. This design increases the volume of the intake chambers 23, thereby reducing intake pressure pulsation.

[0188] like Figure 12 , Figures 15 to 21 , Figures 25 to 30As shown, an exhaust chamber 25 is formed on the outer wall of the cylinder liner 20. 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 60, which effectively reduces the space occupied by the exhaust valve assembly 60, makes the components more rationally arranged, and improves the space utilization of the cylinder liner 20.

[0189] like Figure 16 , Figure 17 and Figure 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 60, 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 60, a large amount of gas leakage in the variable volume chamber 311 is effectively avoided, ensuring the compression efficiency of the variable volume chamber 311.

[0190] like Figure 16 As shown, the exhaust valve assembly 60 is connected to the cylinder liner 20 via fasteners 90. The exhaust valve assembly 60 includes an exhaust valve plate 61 and a valve plate baffle 62. The exhaust valve plate 61 is disposed within the exhaust chamber 25 and blocks the corresponding compressed exhaust port 22. The valve plate baffle 62 overlaps and is disposed on the exhaust valve plate 61. In this way, the valve plate baffle 62 effectively prevents the exhaust valve plate 61 from being over-opened, thereby ensuring the exhaust performance of the cylinder liner 20.

[0191] Optionally, fastener 90 is a screw.

[0192] like Figure 12 and Figure 15 As shown, a connecting hole 26 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 51 is provided, and the connecting hole 26 communicates with the exhaust passage 51. This ensures the reliability of the exhaust of the cylinder liner 20.

[0193] like Figure 15 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.

[0194] like Figure 18 and Figure 19As 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 61 opens, and the compressed gas enters the exhaust chamber 25 through the compression exhaust port 22, passes through the connecting hole 26 on the cylinder liner 20, and is then discharged through the exhaust passage 51 and enters the external space of the pump body assembly 83 (i.e., the compressor cavity), thereby completing the exhaust process.

[0195] Optionally, the exhaust cover 70 is secured to the cylinder liner 20 by fasteners 90.

[0196] Optionally, fastener 90 is a screw.

[0197] Optionally, the outer contour of the exhaust cover 70 is adapted to the outer contour of the exhaust chamber 25.

[0198] The following is a detailed introduction to the operation of the compressor:

[0199] like Figure 3 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.

[0200] 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).

[0201] 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.

[0202] Optionally, the inner wall surface of the cylinder liner 20 has an expansion exhaust chamber, which is connected to the expansion exhaust port.

[0203] Furthermore, the expansion exhaust chamber extends circumferentially around the inner wall of the cylinder by a first preset 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.

[0204] 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.

[0205] 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.

[0206] Example 2

[0207] like Figure 32 and Figure 33 As shown, the difference between this embodiment and Embodiment 1 is that only one end of the axial end of the cylinder liner 20 is provided with a bearing 200, that is, the lower side of the cross groove structure 30 has a bearing 200.

[0208] It should be noted that, in this embodiment, since the bearing 200 is located at one end of the axial end of the cylinder liner 20, the intake and exhaust of the cylinder liner 20 in Embodiment 1 are still applicable.

[0209] Example 3

[0210] like Figure 34 and Figure 35 As shown, the difference between this embodiment and embodiment two is that only one end of the axial end of the cylinder liner 20 is provided with a bearing 200, that is, the upper side of the cross groove structure 30 has a bearing 200.

[0211] It should be noted that, in this embodiment, since the bearing 200 is located at one end of the axial end of the cylinder liner 20, the intake and exhaust of the cylinder liner 20 in Embodiment 1 are still applicable.

[0212] like Figures 36 to 39 As shown, the projection of slider 40 in its sliding direction matches the cross-section of limiting channel 31, wherein, Figure 36 The chamfering of the direction slider and the corresponding cross groove structure 30, Figure 37 The structure consists of a trapezoidal slider and a corresponding cross groove 30. Figure 38 The trapezoidal slider has a chamfered corner and a corresponding cross groove structure 30. Figure 39 It consists of a semi-circular slider with a straight edge and a corresponding cross groove structure 30.

[0213] 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.

[0214] 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.

[0215] 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.

[0216] 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.

[0217] 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.

[0218] 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 with bearings, 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; Bearing (200), at least one bearing (200), the bearing (200) is disposed inside the cylinder liner (20) and located at the axial end of the cylinder liner (20), and the outer ring of the bearing (200) is in contact with the inner wall of the cylinder liner (20); A cross-groove structure (30) is rotatably disposed within the cylinder liner (20). The outer peripheral surface of the cross-groove structure (30) is in contact with the inner ring of the bearing (200). The cross-groove structure (30) has two limiting channels (31). The two limiting channels (31) 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 (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). 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.

2. The fluid machinery according to claim 1, characterized in that, An annular groove (210) is provided on the axial end face of the cylinder liner (20). The distance by which the bottom of the annular groove (210) extends radially inward along the cylinder liner (20) is equal to the distance between the inner and outer rings of the bearing (200). The bearing (200) is installed in the annular groove (210).

3. The fluid machinery according to claim 1, characterized in that, The bearing (200) is provided only at one end of the axial end of the cylinder liner (20); or, The bearings (200) are provided at both ends of the axial end of the cylinder liner (20).

4. The fluid machinery according to claim 1, characterized in that, The diameter Q of the outer circumference of the cross groove structure (30) and the height N of the bearing (200) satisfy the following condition: 3≤Q / N≤7.

5. The fluid machinery according to claim 1, characterized in that, The eccentricity of the eccentric part (11) is equal to the assembly eccentricity of the crankshaft (10) and the cylinder liner (20).

6. The fluid machinery according to claim 1, characterized in that, Both ends of the limiting channel (31) extend to the outer periphery of the cross groove structure (30).

7. The fluid machinery according to claim 1, characterized in that, The two sliders (40) are respectively concentrically arranged with the two eccentric parts (11). The sliders (40) move in a circular motion around the eccentric parts (11). There is a first rotation gap between the hole wall of the through hole (41) and the eccentric part (11). The range of the first rotation gap is 0.005mm~0.05mm.

8. The fluid machinery according to claim 1, characterized in that, The cross groove structure (30) is coaxially arranged with the cylinder liner (20), and there is a second rotation gap between the outer peripheral surface of the cross groove structure (30) and the inner wall surface of the cylinder liner (20), the second rotation gap being 0.005mm~0.08mm.

9. The fluid machinery according to claim 1, characterized in that, The first included angle A is 160 degrees to 200 degrees; the second included angle B is 80 degrees to 100 degrees.

10. The fluid machinery according to claim 1, characterized in that, The fluid machinery also includes a flange (50) disposed at the axial end of the cylinder liner (20), and the crankshaft (10) is concentrically disposed with the flange (50).

11. The fluid machinery according to claim 10, characterized in that, There is a first assembly gap between the crankshaft (10) and the flange (50), the first assembly gap being in the range of 0.005mm to 0.05mm.

12. The fluid machinery according to claim 11, characterized in that, The first assembly gap ranges from 0.01 to 0.03 mm.

13. The fluid machinery according to claim 1, characterized in that, The eccentric part (11) has an arc surface, and the central angle of the arc surface is greater than or equal to 180 degrees.

14. The fluid machinery according to claim 1, characterized in that, The eccentric part (11) is cylindrical.

15. The fluid machinery according to claim 14, characterized in that, The proximal end of the eccentric portion (11) is flush with the outer circle of the shaft portion (12) of the crankshaft (10); or, The proximal end of the eccentric portion (11) protrudes beyond the outer circle of the shaft portion (12) of the crankshaft (10); or, The proximal end of the eccentric portion (11) is located inside the outer circle of the shaft portion (12) of the crankshaft (10).

16. The fluid machinery according to claim 1, characterized in that, The slider (40) includes multiple substructures, which are spliced ​​together to form the through hole (41).

17. The fluid machinery according to claim 1, characterized in that, The two eccentric portions (11) are spaced apart axially on the crankshaft (10).

18. The fluid machinery according to claim 1, characterized in that, The cross groove structure (30) has a central hole (32), and the two limiting channels (31) are connected through the central hole (32). The diameter of the central hole (32) is larger than the diameter of the shaft portion (12) of the crankshaft (10).

19. The fluid machinery according to claim 18, characterized in that, The diameter of the central hole (32) is larger than the diameter of the eccentric part (11).

20. The fluid machinery according to claim 1, characterized in that, 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).

21. The fluid machinery according to claim 1, characterized in that, The slider (40) has 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) facing the variable volume cavity (311).

22. The fluid machinery according to claim 21, characterized in that, 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).

23. The fluid machinery according to claim 22, characterized in that, The radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner (20); or, 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.

24. The fluid machinery according to claim 23, characterized in that, The difference ranges from -0.02 to 0.02 mm.

25. The fluid machinery according to claim 21, characterized in that, The projected area S of the extrusion surface (42) in the sliding direction of the slider (40) 滑块 The area of ​​the compression exhaust port (22) of the cylinder liner (20) is S 排 The following conditions must be met between them: S 滑块 / S 排 The value is 8~25.

26. The fluid machinery according to claim 25, characterized in that, S 滑块 / S 排 The value is 12~18.

27. The fluid machinery according to claim 1, characterized in that, The diameter R of the outer circumference of the cross groove structure (30) and the height N of the bearing (200) satisfy the following condition: 1.5≤R / N≤3.

5.

28. The fluid machinery according to claim 1, characterized in that, The cylinder liner (20) has a compression intake port (21) and a compression exhaust port (22). When any of the sliders (40) is in the air intake position, the compression air intake (21) is connected to the corresponding variable volume cavity (311); When any of the sliders (40) is in the exhaust position, the corresponding variable volume chamber (311) is connected to the compression exhaust port (22).

29. The fluid machinery according to claim 28, characterized in that, The inner wall of the cylinder liner (20) has an intake chamber (23), which is connected to the compression inlet (21).

30. The fluid machinery according to claim 29, 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).

31. The fluid machinery according to claim 29, 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). Both intake chambers (23) are connected to the intake communication chamber (24), and the compression inlet (21) is connected to the intake chamber (23) through the intake communication chamber (24).

32. The fluid machinery according to claim 31, characterized in that, The intake communication cavity (24) extends a second preset distance along the axial direction of the cylinder liner (20).

33. The fluid machinery according to claim 29, 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 compression inlets (21), which are arranged in correspondence with and connected to the two intake chambers (23).

34. The fluid machinery according to claim 28, characterized in that, An exhaust chamber (25) is provided on the outer wall of the cylinder liner (20). The compressed exhaust port (22) is connected to the exhaust chamber (25) through 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 corresponds to the compressed exhaust port (22).

35. The fluid machinery according to claim 34, characterized in that, There are two compressed exhaust ports (22), which are spaced apart along the axial direction of the cylinder liner (20). There are two sets of exhaust valve assemblies (60), which are respectively set to correspond to the two compressed exhaust ports (22).

36. The fluid machinery according to claim 35, characterized in that, The cylinder liner (20) is also provided with a connecting hole (26) on its axial end face. The connecting hole (26) is connected to the exhaust chamber (25). The fluid machinery also includes a flange (50). The flange (50) is provided with an exhaust channel (51). The connecting hole (26) is connected to the exhaust channel (51).

37. The fluid machinery according to claim 34, characterized in that, The exhaust chamber (25) extends to the outer wall of the cylinder liner (20), and the fluid machinery also includes an exhaust cover plate (70), which is connected to the cylinder liner (20) and seals the exhaust chamber (25).

38. The fluid machinery according to any one of claims 28 to 37, characterized in that, The fluid machinery in question is a compressor.

39. The fluid machinery according to claim 1, characterized in that, The cylinder liner (20) has an expansion exhaust port and an expansion intake port. When any of the sliders (40) is in the air intake position, the expansion exhaust port is connected to the corresponding variable volume cavity (311); When any of the sliders (40) is in the exhaust position, the corresponding variable volume chamber (311) is connected to the expansion inlet.

40. The fluid machinery according to claim 39, characterized in that, The inner wall surface of the cylinder liner (20) has an expansion exhaust chamber, which is connected to the expansion exhaust port.

41. The fluid machinery according to claim 40, characterized in that, The expansion exhaust chamber extends circumferentially around the inner wall of the cylinder liner (20) by a first preset distance to form an arc-shaped expansion exhaust chamber. The expansion exhaust chamber extends from the expansion exhaust port to the side where the expansion intake port is located. The extension direction of the expansion exhaust chamber is in the same direction as the rotation direction of the cross groove structure (30).

42. The fluid machinery according to claim 41, characterized in that, 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. Both expansion exhaust chambers are connected to the expansion exhaust communication chamber, and the expansion exhaust port is connected to the expansion exhaust chamber through the expansion exhaust communication chamber.

43. The fluid machinery according to claim 42, characterized in that, The expansion exhaust communication cavity extends a second preset distance along the axial direction of the cylinder liner (20), and at least one end of the expansion exhaust communication cavity penetrates the axial end face of the cylinder liner (20).

44. The fluid machinery according to any one of claims 39 to 43, characterized in that, The fluid machinery in question is an expander.

45. 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 44.

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