Fluid machinery and heat exchange equipment

Abstract

This invention provides a fluid machine and a heat exchange device. The fluid machine includes a crankshaft, a cylinder liner, a cross-groove structure, sliders, and two flanges. The crankshaft has two eccentric portions; the crankshaft and cylinder liner are eccentrically positioned with a fixed eccentricity. The cross-groove structure is rotatably disposed within the cylinder liner, and two limiting channels of the cross-groove structure are sequentially arranged along the axial direction of the crankshaft, with the extension direction of the limiting channels perpendicular to the axial direction of the crankshaft. The two eccentric portions extend into two through holes of the two sliders, and the two sliders are slidably disposed within the two limiting channels, forming variable volume cavities. The two flanges are respectively disposed at both axial ends of the cylinder liner, one of which has an intake channel. The cylinder liner has a radial suction port, and the intake channel and radial suction port are respectively connected to the two variable volume cavities. This invention solves the problems of low energy efficiency, high noise, and insufficient air intake 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 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, existing compressors suffer from insufficient air intake, which leads to increased air intake losses. 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, high noise, and insufficient air intake of compressors in the prior art.

[0006] To achieve the above objectives, according to one aspect of the present invention, a fluid machine is provided, comprising a crankshaft, a cylinder liner, a cross-groove structure, a slider, and two flanges, 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, the cross-groove structure having two limiting channels, the two limiting channels being sequentially arranged along the axial direction of the crankshaft, 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 forming 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; the two flanges are respectively disposed at both ends of the axial direction of the cylinder liner, one of the two flanges having an intake channel, the cylinder liner having a radial intake hole, the intake channel and the radial intake hole respectively communicating with the two variable volume cavities.

[0007] Furthermore, the ratio S / V of the cross-sectional area S of the intake passage to the displacement V of the fluid machinery ranges from 0.001 to 0.6; the ratio S1 / S between the cross-sectional area S1 of the radial intake hole and the cross-sectional area S of the intake passage ranges from 0.2 to 3.

[0008] Furthermore, the inner wall of the cylinder liner has two intake chambers, which are spaced apart along the axial direction of the cylinder liner. The intake passage is connected to the variable volume chamber through the intake chamber on the corresponding side of the two intake chambers, and the radial intake hole is connected to the variable volume chamber through the intake chamber on the corresponding side of the two intake chambers.

[0009] 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.

[0010] Furthermore, the intake passage includes a radial passage section and an axial passage section connected in sequence, and the cylinder liner also has an intake communication cavity, which is only connected to the intake cavity for communicating with the intake passage. The intake communication cavity extends a second preset distance along the axial direction of the cylinder liner, and one end of the intake communication cavity passes through the axial end face of the cylinder liner and communicates with the axial passage section.

[0011] Furthermore, the intake passage includes a radial passage section and an axial passage section connected in sequence. The cylinder liner also has an intake communication cavity. Both intake cavities are connected to the intake communication cavity. The intake communication cavity extends along the axial direction of the cylinder liner by a third preset distance, and one end of the intake communication cavity passes through the axial end face of the cylinder liner and is connected to the axial passage section.

[0012] Furthermore, the radial passage section is positioned circumferentially on the flange, which coincides with the radial intake port position circumferentially on the cylinder liner.

[0013] Furthermore, the channel diameter D of the radial channel section is equal to the diameter D1 of the radial intake hole.

[0014] Furthermore, the channel diameter D of the radial channel section is not equal to the diameter D1 of the radial intake hole.

[0015] Furthermore, the diameter D of the radial channel section and the skirt height H of the flange must satisfy: ≥0.5mm.

[0016] Furthermore, the diameter D1 of the radial intake port and the axial height H1 of the cylinder liner must satisfy: ≥0.5mm.

[0017] Furthermore, exhaust channels are provided on the end faces of both flanges, and the two exhaust channels are respectively connected to the variable volume chambers on the corresponding sides.

[0018] Furthermore, the end of the radial intake port is the first compression intake port, the end of the intake channel is the second compression intake port, and the initial ends of both exhaust channels are compression exhaust ports. When the slider on the side corresponding to the radial intake port is in the intake position, the first compression intake port is connected to the corresponding variable volume chamber. When the slider on the side corresponding to the radial intake port is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side. When the slider on the side corresponding to the intake channel is in the intake position, the second compression intake port is connected to the corresponding variable volume chamber. When the slider on the side corresponding to the intake channel is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side.

[0019] Furthermore, the fluid machinery is the compressor.

[0020] Furthermore, the end of the radial intake hole is the first expansion exhaust port, the end of the intake channel is the second expansion exhaust port, and the initial ends of both exhaust channels are expansion intake ports. When the slider on the side corresponding to the radial intake hole is in the intake position, the first expansion exhaust port is connected to the corresponding variable volume cavity. When the slider on the side corresponding to the radial intake hole is in the exhaust position, the corresponding variable volume cavity is connected to the expansion intake port on the corresponding side. When the slider on the side corresponding to the intake channel is in the intake position, the second expansion exhaust port is connected to the corresponding variable volume cavity. When the slider on the side corresponding to the intake channel is in the exhaust position, the corresponding variable volume cavity is connected to the expansion intake port on the corresponding side.

[0021] Furthermore, the fluid machinery is the expander.

[0022] Furthermore, an exhaust chamber is provided on the outer wall of the cylinder liner, and the cylinder liner also has an exhaust port. The exhaust port is connected to the exhaust chamber by 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 exhaust port.

[0023] Furthermore, there are two exhaust ports, which are spaced apart along the axial direction of the cylinder liner. There are two sets of exhaust valve assemblies, each set corresponding to one of the two exhaust ports.

[0024] Furthermore, at least one axial end face of the cylinder liner is provided with a connecting hole, which communicates with the exhaust chamber. An exhaust passage is provided on the flange opposite to the connecting hole, and the connecting hole communicates with the exhaust passage.

[0025] Furthermore, there is one exhaust port, and the exhaust port is connected to the variable volume cavity on the corresponding side. At least one axial end face of the cylinder liner is also provided with a connecting hole, which is connected to the exhaust cavity. The flange opposite to the connecting hole in the two flanges is provided with a first exhaust passage, and the connecting hole is connected to the first exhaust passage. The flange on the side away from the exhaust port in the two flanges has a second exhaust passage, which is connected to the variable volume cavity on the corresponding side.

[0026] 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.

[0027] Furthermore, the end of the radial intake port is the first compression intake port, the end of the intake passage is the second compression intake port, and the exhaust port on the cylinder liner is the compression exhaust port. When the slider on the side corresponding to the radial intake port is in the intake position, the first compression intake port is connected to the corresponding variable volume chamber. When the slider on the side corresponding to the radial intake port is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side. When the slider on the side corresponding to the intake passage is in the intake position, the second compression intake port is connected to the corresponding variable volume chamber. When the slider on the side corresponding to the intake passage is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side.

[0028] Furthermore, the fluid machinery is the compressor.

[0029] Furthermore, the end of the radial intake hole is the first expansion exhaust port, the end of the intake passage is the second expansion exhaust port, and the exhaust port on the cylinder liner is the expansion intake port. When the slider on the side corresponding to the radial intake hole is in the intake position, the first expansion exhaust port is connected to the corresponding variable volume chamber. When the slider on the side corresponding to the radial intake hole is in the exhaust position, the corresponding variable volume chamber is connected to the expansion intake port on the corresponding side. When the slider on the side corresponding to the intake passage is in the intake position, the second expansion exhaust port is connected to the corresponding variable volume chamber. When the slider on the side corresponding to the intake passage is in the exhaust position, the corresponding variable volume chamber is connected to the expansion intake port on the corresponding side.

[0030] Furthermore, the fluid machinery is the expander.

[0031] 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.

[0032] 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.

[0033] By applying the technical solution of this invention, an intake channel is provided on one of the two flanges, and a radial intake hole is provided on the cylinder liner. The intake channel and the radial intake hole are respectively connected to two variable volume chambers. In this way, the air intake reliability of the fluid machinery is ensured, and air intake loss due to insufficient air intake is avoided, thereby ensuring that the volumetric efficiency of the fluid machinery can reach the optimal level. Attached Figure Description

[0034] 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:

[0035] Figure 1 A schematic diagram of the internal structure of a fluid machine according to Embodiment 1 of the present invention is shown;

[0036] Figure 2 It shows Figure 1 A schematic diagram of the pump body assembly of fluid machinery in a fluid machine;

[0037] Figure 3 It shows Figure 2 An exploded view of the pump body components;

[0038] Figure 4 It shows Figure 3 A schematic diagram of the assembly structure of the crankshaft, cross groove structure, and slider;

[0039] Figure 5 It shows Figure 4 A cross-sectional view of the crankshaft, cross groove structure, and slider in the diagram;

[0040] Figure 6 It shows Figure 3 A schematic diagram of the eccentricity of the crankshaft shaft body and the two eccentric parts;

[0041] Figure 7 It shows Figure 3 A cross-sectional structural schematic diagram of the assembly eccentricity of the crankshaft and cylinder liner;

[0042] Figure 8 It shows Figure 3 A structural schematic diagram of the eccentricity between the cylinder liner and the lower flange;

[0043] Figure 9 It shows Figure 3 A schematic diagram of the slider in the through hole along its axial direction;

[0044] Figure 10 It shows Figure 3 A schematic diagram of the upper flange of the pump body assembly;

[0045] Figure 11 It shows Figure 10 A cross-sectional view of the upper flange in the diagram;

[0046] Figure 12 It shows Figure 3 A schematic diagram of the cylinder liner structure of the pump body assembly;

[0047] Figure 13 It shows Figure 12 A cross-sectional view of the cylinder liner;

[0048] Figure 14 It shows Figure 12 A cross-sectional view of the cylinder liner from another perspective;

[0049] Figure 15 It shows Figure 2 A schematic diagram of the non-independent intake structure of the upper flange and cylinder liner of the pump body assembly;

[0050] Figure 16 A schematic diagram of the internal structure of a fluid machine according to Embodiment 2 of the present invention is shown;

[0051] Figure 17 It shows Figure 16 A schematic diagram of the pump body assembly of fluid machinery in a fluid machine;

[0052] Figure 18 It shows Figure 16 An exploded view of the pump body components;

[0053] Figure 19 It shows Figure 18 A schematic diagram of the cylinder liner structure;

[0054] Figure 20 It shows Figure 19 A cross-sectional view of the cylinder liner;

[0055] Figure 21 It shows Figure 18 A schematic diagram of the lower flange in the diagram;

[0056] Figure 22 It shows Figure 21 A cross-sectional view of the lower flange in the diagram;

[0057] Figure 23 It shows Figure 17 A schematic diagram of the non-independent intake structure of the lower flange and cylinder liner of the pump body assembly;

[0058] Figure 24 It shows Figure 17 A schematic diagram of the venting structure of the upper and lower flanges of the pump body assembly;

[0059] Figure 25 It shows Figure 17 A schematic diagram of the cylinder liner side exhaust structure of the pump body assembly;

[0060] Figure 26 It shows Figure 17 A schematic diagram of the combined cylinder liner-side exhaust and flange exhaust structure of the pump body assembly;

[0061] Figure 27 A graph showing the effect of the ratio of the cross-sectional area of ​​the intake passage to the displacement of the fluid machinery on the volumetric efficiency of the compressor.

[0062] Figure 28 A schematic diagram illustrating the operating principle of a compressor according to an optional embodiment of the present invention is shown;

[0063] Figure 29 It shows Figure 28 A schematic diagram illustrating the operating principle of the compressor in the diagram;

[0064] Figure 30 A schematic diagram illustrating the operating principle of a compressor in the prior art is shown;

[0065] Figure 31 A schematic diagram illustrating the operating principle of the improved compressor in the prior art is shown;

[0066] Figure 32 It shows Figure 31 The diagram shows the mechanism of the compressor in operation, which illustrates the lever arm that drives the slider to rotate.

[0067] Figure 33 It shows Figure 31 The diagram shows the operating principle of the compressor mechanism. In this diagram, the center of the limiting groove structure and the center of the eccentric part coincide.

[0068] The above figures include the following reference numerals:

[0069] 10. Crankshaft; 11. Eccentric part; 12. Shaft body section;

[0070] 20. Cylinder liner; 21. Radial intake port; 22. Exhaust port; 23. Intake chamber; 24. Intake connecting chamber; 25. Exhaust chamber; 26. Connecting hole;

[0071] 30. Cross-groove structure; 31. Limiting channel;

[0072] 40. Slider; 41. Through hole; 42. Extrusion surface;

[0073] 50. Flange; 51. Exhaust passage; 511. First exhaust passage; 512. Second exhaust passage; 52. Upper flange; 53. Lower flange; 54. Intake passage; 541. Radial passage section; 542. Axial passage section;

[0074] 80. Dispenser component; 81. Housing assembly; 82. Motor assembly; 83. Pump body assembly; 84. Upper cover assembly; 85. Lower cover assembly. Detailed Implementation

[0075] 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.

[0076] In existing technologies, such as Figure 30 As shown, a compressor operating mechanism principle is proposed based on the cross slider mechanism. Specifically, point O1 is used as the cylinder center, point O2 as the drive shaft center, and point O3 as the slider center. The cylinder and drive shaft are eccentrically set, and the slider center O3 moves in a circle with a diameter of O1O2.

[0077] 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.

[0078] Because the midpoint O0 of line segment O1O2 is a virtual center, a balancing system cannot be set up, leading to a deterioration of the compressor's high-frequency vibration characteristics. Based on the above operating mechanism principle, as follows... Figure 31 As shown, a motion mechanism with O0 as the center of the drive shaft is proposed. That is, the cylinder center O1 and the drive shaft center O0 are the two rotation centers of the motion mechanism. The drive shaft has an eccentric part, and the slider is coaxially arranged with the eccentric part. The assembly eccentricity of the drive shaft and the cylinder is equal to the eccentricity of the eccentric part, so that the slider center O3 moves in a circle with the drive shaft center O0 as the center and O1O0 as the radius.

[0079] 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.

[0080] However, as Figure 32As shown, the length of the lever arm L that drives the slider to rotate is L = 2e × cosθ × cosθ, where e is the eccentricity of the eccentric part and θ is the angle between the line connecting O1O0 and the sliding direction of the slider in the limiting groove.

[0081] like Figure 33 As shown, when the cylinder center O1 (i.e., the center of the limiting groove structure) coincides with the center of the eccentric part, the resultant force of the driving force of the drive shaft passes through the center of the limiting groove structure. That is, the torque applied to the limiting groove structure is zero, the limiting groove structure cannot rotate, and the motion mechanism is at a dead point position and cannot drive the slider to rotate.

[0082] 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.

[0083] To address the problems of low energy efficiency and high noise in existing compressors, this invention provides a fluid machine, a heat exchange device, and a method for operating the fluid machine, wherein the heat exchange device includes the fluid machine described below, and the fluid machine is operated using the method described below.

[0084] The fluid machinery of this invention includes a crankshaft 10, a cylinder liner 20, a cross-groove structure 30, and a slider 40. The crankshaft 10 has two eccentric portions 11 arranged along its axial direction, with a phase difference of a first included angle A between them, and the eccentricity of the two eccentric portions 11 is equal. The crankshaft 10 and the cylinder liner 20 are eccentrically arranged with a fixed eccentric distance. The cross-groove structure 30 is rotatably disposed within the cylinder liner 20 and has two limiting channels 31. The two limiting channels 31 are sequentially arranged along the axial direction of the crankshaft 10, and the extending direction of the limiting channels 31 is perpendicular to the axial direction of the crankshaft 10. The extension directions of the positioning channels 31 have a phase difference of a second included angle B, wherein the first included angle A is twice the second included angle B; the slider 40 has a through hole 41, and there are two sliders 40. The two eccentric parts 11 extend into the two through holes 41 of the two sliders 40 respectively. The two sliders 40 are slidably disposed in the two limiting channels 31 and form a variable volume cavity. The variable volume cavity is located in the sliding direction of the slider 40. The crankshaft 10 rotates to drive the slider 40 to slide back and forth in the limiting channel 31 while interacting with the cross groove structure 30, so that the cross groove structure 30 and the slider 40 rotate in the cylinder liner 20.

[0085] By configuring the cross-groove structure 30 into a structure with two limiting channels 31 and correspondingly arranging two sliders 40, the two eccentric portions 11 of the crankshaft extend into the two through holes 41 of the two sliders 40. Simultaneously, the two sliders 40 are slidably disposed within the two limiting channels 31, forming a variable volume cavity. Since the first included angle A between the two eccentric portions 11 is twice the second included angle B between the extending directions of the two limiting channels 31, when one of the two sliders 40 is at a dead position, that is, the driving torque of the eccentric portion 11 corresponding to the slider 40 at the dead position is 0. When the slider 40 is at its dead point, it cannot continue to rotate. At this time, the driving torque of the other eccentric part 11 driving the corresponding slider 40 is at its maximum value, ensuring that the eccentric part 11 with the maximum driving torque can drive the corresponding slider 40 to rotate normally. This slider 40 drives the cross groove structure 30 to rotate, and then the cross groove structure 30 drives the slider 40 at its dead point to continue to rotate. This achieves stable operation of the fluid machinery, avoids the dead point of the motion mechanism, improves the motion reliability of the fluid machinery, and thus ensures the working reliability of the heat exchange equipment.

[0086] 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.

[0087] It should be noted that in this application, neither the first included angle A nor the second included angle B is zero.

[0088] like Figure 28 and Figure 29As shown, when the aforementioned fluid machinery is running, the crankshaft 10 rotates around its axis O0; the cross-groove structure 30 revolves around the axis O0 of the crankshaft 10, with the axis O0 of the crankshaft 10 and the axis O1 of the cross-groove structure 30 being eccentrically positioned with a fixed eccentricity; the first slider 40 moves in a circular motion with the axis O0 of the crankshaft 10 as its center, and the distance between the center O3 of the first slider 40 and the axis O0 of the crankshaft 10 is equal to the eccentricity of the first eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentricity between the axis O0 of the crankshaft 10 and the axis O1 of the cross-groove structure 30. The crankshaft 10 rotates to drive the first slider 40 to move in a circular motion. The first slider 40 interacts with the cross groove structure 30 and slides back and forth within the limiting channel 31 of the cross groove structure 30; the second slider 40 makes a circular motion with the axis O0 of the crankshaft 10 as the center, and the distance between the center O4 of the second slider 40 and the axis O0 of the crankshaft 10 is equal to the eccentricity of the second eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentric distance between the axis O0 of the crankshaft 10 and the axis O1 of the cross groove structure 30. The crankshaft 10 rotates to drive the second slider 40 to make a circular motion, and the second slider 40 interacts with the cross groove structure 30 and slides back and forth within the limiting channel 31 of the cross groove structure 30.

[0089] The fluid machinery operating as described above constitutes a cross-slider mechanism. This operating method adopts the principle of a cross-slider mechanism, wherein the two eccentric portions 11 of the crankshaft 10 serve as the first connecting rod L1 and the second connecting rod L2, respectively, and the two limiting channels 31 of the cross groove structure 30 serve as the third connecting rod L3 and the fourth connecting rod L4, respectively, and the lengths of the first connecting rod L1 and the second connecting rod L2 are equal (please refer to...). Figure 28 ).

[0090] like Figure 28 As shown, there is a first included angle A between the first link L1 and the second link L2, and a second included angle B between the third link L3 and the fourth link L4, wherein the first included angle A is twice the second included angle B.

[0091] like Figure 29 As shown, the line connecting the axis O0 of crankshaft 10 and the axis O1 of cross groove structure 30 is line O0O1. The first connecting rod L1 has a third included angle C with line O0O1, and the corresponding third connecting rod L3 has a fourth included angle D with line O0O1, wherein the third included angle C is twice the fourth included angle D; the second connecting rod L2 has a fifth included angle E with line O0O1, and the corresponding fourth connecting rod L4 has a sixth included angle F with line O0O1, wherein the fifth included angle E is twice the sixth included angle F; the sum of the third included angle C and the fifth included angle E is the first included angle A, and the sum of the fourth included angle D and the sixth included angle F is the second included angle B.

[0092] 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.

[0093] 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.

[0094] It should be noted that, in this application, the maximum lever arm of the driving torque of the eccentric part 11 is 2e.

[0095] 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.

[0096] 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.

[0097] To address the problems of low energy efficiency and high noise in existing compressors, 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.

[0098] like Figures 1 to 15As 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. 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.

[0099] Specifically, such as Figure 6 As shown, the eccentricity of both eccentric parts 11 is equal to e, as... Figure 7 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 8 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.

[0100] 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.

[0101] Preferably, the range of the first assembly gap is 0.01 to 0.03 mm.

[0102] 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.

[0103] Optionally, a second rotational clearance is provided between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder liner 20, the size of which is 0.005mm to 0.1mm.

[0104] like Figures 1 to 7 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.

[0105] 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.

[0106] Optionally, the first and second sections can be detachably connected. This ensures ease of assembly and disassembly of the crankshaft 10.

[0107] like Figures 1 to 7 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.

[0108] 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.

[0109] like Figure 3 and Figure 4 As shown, both ends of the limiting channel 31 extend to the outer peripheral surface of the cross groove structure 30. This helps to reduce the processing and manufacturing difficulty of the cross groove structure 30.

[0110] 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.

[0111] Preferably, the first included angle A is 160 degrees and the second included angle B is 80 degrees.

[0112] Preferably, the first included angle A is 165 degrees and the second included angle B is 82.5 degrees.

[0113] Preferably, the first included angle A is 170 degrees and the second included angle B is 85 degrees.

[0114] Preferably, the first included angle A is 175 degrees and the second included angle B is 87.5 degrees.

[0115] Preferably, the first included angle A is 180 degrees and the second included angle B is 90 degrees.

[0116] Preferably, the first included angle A is 185 degrees and the second included angle B is 92.5 degrees.

[0117] Preferably, the first included angle A is 190 degrees and the second included angle B is 95 degrees.

[0118] Preferably, the first included angle A is 195 degrees and the second included angle B is 97.5 degrees.

[0119] 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.

[0120] like Figures 1 to 7 As shown, the eccentric part 11 is cylindrical.

[0121] Optionally, the proximal end of the eccentric portion 11 is flush with the outer circle of the shaft portion 12 of the crankshaft 10.

[0122] Optionally, the proximal end of the eccentric portion 11 protrudes beyond the outer circle of the shaft portion 12 of the crankshaft 10.

[0123] Optionally, the proximal end of the eccentric portion 11 is located inside the outer circle of the shaft portion 12 of the crankshaft 10.

[0124] 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.

[0125] like Figures 1 to 7 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.

[0126] It should be noted that in this application, the cross-groove structure 30 has a central hole, through which the two limiting channels 31 are connected. The diameter of the central hole 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.

[0127] Optionally, the diameter of the central hole 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.

[0128] like Figure 9 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. 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.

[0129] 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 9 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 9 The dashed X-line in the diagram represents the circle containing the center of the two arc surfaces.

[0130] Optionally, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner 20.

[0131] 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.

[0132] Preferably, the difference ranges from -0.02 to 0.02 mm.

[0133] 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 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.

[0134] Preferably, S 滑块 / S 排 The value is 12 to 18.

[0135] 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.

[0136] Furthermore, such as Figure 1 As shown, the separator component 80 has two suction tubes, which are used to communicate with the radial suction port 21 and the air inlet channel 54, respectively.

[0137] Alternatively, the above-mentioned components can be connected by welding, heat fitting, or cold pressing.

[0138] 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 .

[0139] It should be noted that in this embodiment, the enclosed space formed by the slider 40, the limiting channel 31, the cylinder liner 20 and the upper flange 52 (or lower flange 53) is the variable volume chamber. The pump body assembly 83 has a total of 4 variable volume chambers. During the rotation of the crankshaft 10, the crankshaft 10 rotates 2 revolutions, and a single variable volume chamber completes 1 intake and exhaust process. For the compressor, the crankshaft 10 rotates 2 revolutions, and a total of 4 intake and exhaust processes are completed.

[0140] 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.

[0141] To address the problem of insufficient compressor suction, this invention supplements the aforementioned fluid machinery with the following details:

[0142] Example 1

[0143] like Figures 1 to 15 As shown, the fluid machinery also includes two flanges 50, which are respectively disposed at both ends of the cylinder liner 20. One of the two flanges 50 has an air intake passage 54, and the cylinder liner 20 has a radial air intake hole 21. The air intake passage 54 and the radial air intake hole 21 are respectively connected to two variable volume chambers.

[0144] By providing an intake channel 54 on one of the two flanges 50, and a radial intake hole 21 on the cylinder liner 20, and by connecting the intake channel 54 and the radial intake hole 21 to the two variable volume chambers respectively, the air intake reliability of the fluid machinery is ensured, and the air intake loss caused by insufficient air intake is avoided, thereby ensuring that the volumetric efficiency of the fluid machinery can reach the optimal level.

[0145] In addition, by setting an intake channel 54 and a radial suction hole 21 on the flange 50 and cylinder liner 20 respectively, the compressor is ensured to draw in sufficient air, thereby improving the performance and cooling capacity of the compressor. This solves the problem of mutual interference between various structures due to the small size, making the design of the compressor easier.

[0146] It should be noted that, in this embodiment, an air intake channel 54 is provided on the upper flange 52.

[0147] Preferably, the ratio S / V of the cross-sectional area S of the intake passage 54 to the displacement V of the fluid machinery ranges from 0.001 to 0.6; the ratio S1 / S of the cross-sectional area S1 of the radial intake port 21 to the cross-sectional area S of the intake passage 54 ranges from 0.2 to 3. Thus, by rationally optimizing the range of the ratio S / V of the cross-sectional area S of the radial intake port 21 to the displacement V of the fluid machinery, it is beneficial to reduce insufficient compressor intake and intake losses, thereby improving compressor performance.

[0148] like Figure 27 The graph shows the effect of the ratio of the cross-sectional area of ​​the intake passage 54 to the displacement V of the fluid machinery on the volumetric efficiency of the compressor. It can be seen from the graph that the compressor's volumetric efficiency is optimal when the S / V ratio is within the range of 0.001 to 0.6.

[0149] like Figure 2 , Figure 13 and Figure 15 As shown, the inner wall of the cylinder liner 20 has two intake chambers 23, which are spaced apart along the axial direction of the cylinder liner 20. The intake passage 54 communicates with the variable volume chamber through the corresponding side of the intake chamber 23, and the radial intake hole 21 communicates with the variable volume chamber through the corresponding side of the intake chamber 23. This ensures that the intake chamber 23 can store a large amount of gas, allowing the variable volume chamber to be fully saturated, thus enabling the compressor to draw in sufficient gas. Furthermore, when intake is insufficient, the stored gas can be supplied to the variable volume chamber in a timely manner to ensure the compressor's compression efficiency.

[0150] 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.

[0151] 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.

[0152] like Figure 2 and Figure 11As shown, the intake passage 54 includes a radial passage section 541 and an axial passage section 542 connected in sequence. The cylinder liner 20 also has an intake communication cavity 24, which is only connected to the intake cavity 23 for communicating with the intake passage 54. The intake communication cavity 24 extends along the axial direction of the cylinder liner 20 by a second predetermined distance, and one end of the intake communication cavity 24 penetrates the axial end face of the cylinder liner 20 and communicates with the axial passage section 542. In this way, the intake reliability of the intake passage 54 is ensured. At the same time, the intake passage 54 and the radial intake port 21 of the cylinder liner 20 are able to intake independently, ensuring that the intake processes of the intake passage 54 and the radial intake port 21 do not interfere with each other.

[0153] like Figure 15 As shown, the intake passage 54 includes a radial passage section 541 and an axial passage section 542 connected in sequence. The cylinder liner 20 also has an intake communication cavity 24. Both intake chambers 23 are connected to the intake communication cavity 24. The intake communication cavity 24 extends along the axial direction of the cylinder liner 20 by a third predetermined distance, and one end of the intake communication cavity 24 penetrates the axial end face of the cylinder liner 20 and is connected to the axial passage section 542. In this way, the intake reliability of the intake passage 54 is ensured, and at the same time, the intake passage 54 and the radial intake port 21 of the cylinder liner 20 are not independently connected for intake.

[0154] It should be noted that when the displacement of the upper and lower parts of cylinder liner 20 is not equal, it can be achieved by... Figure 15 The compressor uses a non-independent intake method to ensure sufficient intake.

[0155] like Figure 3 As shown, the radial channel section 541 is positioned in the circumferential direction of the flange 50, which coincides with the position of the radial intake port 21 in the circumferential direction of the cylinder liner 20.

[0156] like Figure 11 and Figure 13 As shown, the channel diameter D of the radial channel section 541 is equal to the hole diameter D1 of the radial intake hole 21.

[0157] Of course, the channel diameter D of the radial channel section 541 and the hole diameter D1 of the radial intake hole 21 may not be equal.

[0158] like Figure 11 As shown, the channel diameter D of the radial channel section 541 and the skirt height H of the flange 50 satisfy the following condition: H / 2 - D / 2 ≥ 0.5 mm. This ensures sufficient air intake for the compressor while guaranteeing that the flange 50 has sufficient structural strength.

[0159] like Figure 13As shown, the diameter D1 of the radial intake hole 21 and the axial height H1 of the cylinder liner 20 satisfy the following condition: H1 / 2 - D1 / 2 ≥ 0.5 mm. This ensures sufficient intake for the compressor while guaranteeing that the cylinder liner 20 has sufficient structural strength.

[0160] Example 2

[0161] It should be noted that the difference between this embodiment and Embodiment 1 is that, as shown in the following... Figures 16 to 23 As shown, an air intake channel 54 is provided on the lower flange 53 in this embodiment. Other features are similar and will not be described in detail here.

[0162] like Figure 23 As shown, the intake passage 54 and the radial intake port 21 of the cylinder liner 20 are not independent intake ports. When the displacement of the upper and lower parts of the cylinder liner 20 is not equal, it can be controlled by... Figure 23 The compressor uses a non-independent intake method to ensure sufficient intake.

[0163] The following description uses the compressor in Example 2 as an example to illustrate the compressor's exhaust process:

[0164] In the first exhaust embodiment, flange exhaust is performed on the upper flange 52 and the lower flange 53:

[0165] like Figure 24 As shown, exhaust channels 51 are provided on the end faces of both flanges 50, and the two exhaust channels 51 are respectively connected to the variable volume cavities on the corresponding sides. In this way, the two exhaust channels 51 are respectively opened on the planes of the upper flange 52 and the lower flange 53, rather than on the curved surface of the side wall of the cylinder liner 20, which greatly reduces the difficulty of machining and manufacturing the exhaust channels 51.

[0166] Taking the compressor as an example, the end of the radial suction port 21 is the first compression inlet, the end of the intake channel 54 is the second compression inlet, and the initial ends of the two exhaust channels 51 are both compression exhaust ports. When the slider 40 on the side corresponding to the radial suction port 21 is in the intake position, the first compression inlet is connected to the corresponding variable volume chamber. When the slider 40 on the side corresponding to the radial suction port 21 is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side. When the slider 40 on the side corresponding to the intake channel 54 is in the intake position, the second compression inlet is connected to the corresponding variable volume chamber. When the slider 40 on the side corresponding to the intake channel 54 is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side.

[0167] Other applications: By swapping the positions of the first compression inlet, the second compression inlet, and the compression outlet, this compressor can be used as an expander. That is, the compressor's compression outlet 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 first compression inlet (first expansion outlet) and second compression inlet (second expansion outlet).

[0168] Specifically, the end of the radial intake hole 21 is the first expansion exhaust port, the end of the intake channel 54 is the second expansion exhaust port, and the initial ends of both exhaust channels 51 are expansion intake ports. When the slider 40 on the side corresponding to the radial intake hole 21 is in the intake position, the first expansion exhaust port is connected to the corresponding variable volume cavity. When the slider 40 on the side corresponding to the radial intake hole 21 is in the exhaust position, the corresponding variable volume cavity is connected to the expansion intake port on the corresponding side. When the slider 40 on the side corresponding to the intake channel 54 is in the intake position, the second expansion exhaust port is connected to the corresponding variable volume cavity. When the slider 40 on the side corresponding to the intake channel 54 is in the exhaust position, the corresponding variable volume cavity is connected to the expansion intake port on the corresponding side.

[0169] Optionally, the inner wall surface of the cylinder liner 20 has an expansion exhaust chamber, which is connected to the expansion exhaust port.

[0170] 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.

[0171] 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.

[0172] 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.

[0173] Exhaust Example 2: Exhaust from cylinder liner 20 side:

[0174] like Figure 25As shown, an exhaust chamber 25 is formed on the outer wall of the cylinder liner 20. The cylinder liner 20 also has an exhaust port 22, which 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, which is disposed in the exhaust chamber 25 and corresponding to the 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.

[0175] like Figure 25 As shown, there are two 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 exhaust ports 22. In this way, since each of the two exhaust ports 22 is equipped with a separate set of exhaust valve assemblies, a large amount of gas leakage in the variable volume chamber is effectively avoided, thus ensuring the compression efficiency of the variable volume chamber.

[0176] like Figure 25 As shown, at least one axial end face of the cylinder liner 20 is provided with a connecting hole 26, which communicates with the exhaust chamber 25. An exhaust passage 51 is provided on the flange 50 opposite to the connecting hole 26, and the connecting hole 26 communicates with the exhaust passage 51. This ensures the reliability of the exhaust from the cylinder liner 20.

[0177] It should be noted that in this embodiment, an exhaust channel 51 is provided on the upper flange 52. Of course, an exhaust channel 51 can also be provided on the lower flange 53, or even on both the upper flange 52 and the lower flange 53. The appropriate channel can be selected according to the requirements.

[0178] Exhaust embodiment three: Exhaust from cylinder liner 20 side combined with exhaust from one of the two flanges 50:

[0179] like Figure 26 As shown, there is one exhaust port 22, which is connected to the corresponding variable volume cavity. At least one axial end face of the cylinder liner 20 is also provided with a connecting hole 26, which is connected to the exhaust cavity 25. One of the two flanges 50 opposite to the connecting hole 26 has a first exhaust passage 511, which is connected to the connecting hole 26. The flange 50 furthest from the exhaust port 22 has a second exhaust passage 512, which is connected to the corresponding variable volume cavity. This achieves exhaust from the cylinder liner 20 side and exhaust from one end face of the two flanges 50, ensuring the reliability of the compressor's exhaust.

[0180] It should be noted that in this application, the exhaust chamber 25 extends to the outer wall of the cylinder liner 20, and the fluid machinery also includes an exhaust cover plate, which is connected to the cylinder liner 20 and seals the exhaust chamber 25. In this way, the exhaust cover plate serves to separate the variable volume chamber from the external space of the pump body assembly 83.

[0181] Taking a compressor as an example, the end of the radial intake port 21 is the first compression intake port, the end of the intake channel 54 is the second compression intake port, and the exhaust port 22 on the cylinder liner 20 is the compression exhaust port. When the slider 40 on the side corresponding to the radial intake port 21 is in the intake position, the first compression intake port is connected to the corresponding variable volume chamber. When the slider 40 on the side corresponding to the radial intake port 21 is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side. When the slider 40 on the side corresponding to the intake channel 54 is in the intake position, the second compression intake port is connected to the corresponding variable volume chamber. When the slider 40 on the side corresponding to the intake channel 54 is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side.

[0182] Other applications: By swapping the positions of the first compression inlet, the second compression inlet, and the exhaust port, 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 first compression inlet (first expansion exhaust port) and second compression inlet (second expansion exhaust port).

[0183] Specifically, the end of the radial intake port 21 is the first expansion exhaust port, the end of the intake passage 54 is the second expansion exhaust port, and the exhaust port 22 on the cylinder liner 20 is the expansion intake port. When the slider 40 on the side corresponding to the radial intake port 21 is in the intake position, the first expansion exhaust port is connected to the corresponding variable volume chamber. When the slider 40 on the side corresponding to the radial intake port 21 is in the exhaust position, the corresponding variable volume chamber is connected to the expansion intake port on the corresponding side. When the slider 40 on the side corresponding to the intake passage 54 is in the intake position, the second expansion exhaust port is connected to the corresponding variable volume chamber. When the slider 40 on the side corresponding to the intake passage 54 is in the exhaust position, the corresponding variable volume chamber is connected to the expansion intake port on the corresponding side.

[0184] 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.

[0185] 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.

[0186] 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.

[0187] 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.

[0188] 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.

[0189] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A fluid machine, characterized in that, include: A crankshaft (10) having two eccentric portions (11) along its axial direction; Cylinder liner (20), the crankshaft (10) and the cylinder liner (20) are eccentrically arranged and the eccentric distance is fixed; A cross-groove structure (30) is rotatably disposed within the cylinder liner (20). The cross-groove structure (30) has two limiting channels (31), which are arranged sequentially along the axial direction of the crankshaft (10). The extending direction of the limiting channels (31) is perpendicular to the axial direction of the crankshaft (10). The slider (40) has a through hole (41). There are two sliders (40). The two eccentric parts (11) extend into the two through holes (41) of the two sliders (40). The two sliders (40) are slidably disposed in the two limiting channels (31) and form a variable volume cavity. The variable volume cavity is located in the sliding direction of the slider (40). The crankshaft (10) rotates to drive the slider (40) to slide back and forth in the limiting channel (31) while interacting with the cross groove structure (30), so that the cross groove structure (30) and the slider (40) rotate in the cylinder liner (20). Two flanges (50) are respectively disposed at both ends of the cylinder liner (20). One of the two flanges (50) has an intake passage (54). The cylinder liner (20) has a radial intake hole (21). The intake passage (54) and the radial intake hole (21) are respectively connected to the two variable volume cavities. The ratio S / V of the cross-sectional area S of the intake channel (54) to the displacement V of the fluid machinery is in the range of 0.001~0.

6.

2. The fluid machinery according to claim 1, characterized in that, The ratio S1 / S between the cross-sectional area S1 of the radial intake hole (21) and the cross-sectional area S of the intake channel (54) is in the range of 0.2 to 3.

3. The fluid machinery according to claim 1, characterized in that, The inner wall of the cylinder liner (20) has two intake chambers (23), which are spaced apart along the axial direction of the cylinder liner (20). The intake passage (54) is connected to the variable volume chamber through the intake chamber (23) on the corresponding side of the two intake chambers (23), and the radial intake hole (21) is connected to the variable volume chamber through the intake chamber (23) on the corresponding side of the two intake chambers (23).

4. The fluid machinery according to claim 3, 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).

5. The fluid machinery according to claim 3, characterized in that, The intake passage (54) includes a radial passage section (541) and an axial passage section (542) connected in sequence. The cylinder liner (20) also has an intake communication cavity (24). The intake communication cavity (24) is only connected to the intake cavity (23) for communicating with the intake passage (54). The intake communication cavity (24) extends a second preset distance along the axial direction of the cylinder liner (20), and one end of the intake communication cavity (24) penetrates the axial end face of the cylinder liner (20) and communicates with the axial passage section (542).

6. The fluid machinery according to claim 3, characterized in that, The intake passage (54) includes a radial passage section (541) and an axial passage section (542) connected in sequence. The cylinder liner (20) also has an intake communication cavity (24). Both intake cavities (23) are connected to the intake communication cavity (24). The intake communication cavity (24) extends along the axial direction of the cylinder liner (20) by a third preset distance. One end of the intake communication cavity (24) passes through the axial end face of the cylinder liner (20) and is connected to the axial passage section (542).

7. The fluid machinery according to claim 5 or 6, characterized in that, The radial channel segment (541) is positioned in the circumferential direction of the flange (50) and the radial intake hole (21) is positioned in the circumferential direction of the cylinder liner (20).

8. The fluid machinery according to claim 5 or 6, characterized in that, The channel diameter D of the radial channel segment (541) is equal to the hole diameter D1 of the radial air intake hole (21).

9. The fluid machinery according to claim 5 or 6, characterized in that, The channel diameter D of the radial channel segment (541) is not equal to the hole diameter D1 of the radial air intake hole (21).

10. The fluid machinery according to claim 5 or 6, characterized in that, The channel diameter D of the radial channel section (541) and the skirt height H of the flange (50) satisfy the following condition: (H / 2-D / 2)≥0.5mm.

11. The fluid machinery according to claim 5 or 6, characterized in that, The diameter D1 of the radial intake hole (21) and the axial height H1 of the cylinder liner (20) satisfy the following condition: (H1 / 2-D1 / 2)≥0.5mm.

12. The fluid machinery according to claim 1, characterized in that, Both flanges (50) have exhaust channels (51) on their end faces, and the two exhaust channels (51) are respectively connected to the variable volume cavity on the corresponding side.

13. The fluid machinery according to claim 12, characterized in that, The end of the radial intake hole (21) is the first compression intake port, the end of the intake channel (54) is the second compression intake port, and the initial ends of both exhaust channels (51) are compression exhaust ports. When the slider (40) located on the side corresponding to the radial air intake hole (21) is in the air intake position, the first compression air intake port is connected to the corresponding variable volume cavity. When the slider (40) located on the side corresponding to the radial air intake hole (21) is in the exhaust position, the corresponding variable volume cavity is connected to the compression exhaust port on the corresponding side. When the slider (40) located on the side corresponding to the intake channel (54) is in the intake position, the second compression intake port is connected to the corresponding variable volume cavity. When the slider (40) located on the side corresponding to the intake channel (54) is in the exhaust position, the corresponding variable volume cavity is connected to the corresponding compression exhaust port.

14. The fluid machinery according to claim 13, characterized in that, The fluid machinery is a compressor.

15. The fluid machinery according to claim 12, characterized in that, The end of the radial intake hole (21) is the first expansion exhaust port, and the end of the intake channel (54) is the second expansion exhaust port. The initial ends of both exhaust channels (51) are expansion intake ports. When the slider (40) located on the side corresponding to the radial air intake hole (21) is in the air intake position, the first expansion exhaust port is connected to the corresponding variable volume cavity. When the slider (40) located on the side corresponding to the radial air intake hole (21) is in the exhaust position, the corresponding variable volume cavity is connected to the expansion air intake port on the corresponding side. When the slider (40) located on the side corresponding to the air intake channel (54) is in the air intake position, the second expansion exhaust port is connected to the corresponding variable volume cavity. When the slider (40) located on the side corresponding to the air intake channel (54) is in the exhaust position, the corresponding variable volume cavity is connected to the expansion air intake port on the corresponding side.

16. The fluid machinery according to claim 12, characterized in that, The fluid machinery is an expander.

17. The fluid machinery according to claim 1, characterized in that, The cylinder liner (20) has an exhaust chamber (25) on its outer wall. The cylinder liner (20) also has an exhaust port (22). The exhaust port (22) is connected to the exhaust chamber (25) by the inner wall of the cylinder liner (20). The fluid machinery also includes an exhaust valve assembly, which is disposed in the exhaust chamber (25) and is disposed corresponding to the exhaust port (22).

18. The fluid machinery according to claim 17, characterized in that, There are two exhaust ports (22), which are spaced apart along the axial direction of the cylinder liner (20). There are two sets of exhaust valve assemblies, which are respectively set to correspond to the two exhaust ports (22).

19. The fluid machinery according to claim 18, characterized in that, At least one axial end face of the cylinder liner (20) is provided with a connecting hole (26), which is connected to the exhaust chamber (25). An exhaust passage (51) is provided on the flange (50) opposite to the connecting hole (26) of the two flanges (50), and the connecting hole (26) is connected to the exhaust passage (51).

20. The fluid machinery according to claim 17, characterized in that, The exhaust port (22) is one, and the exhaust port (22) is connected to the variable volume cavity on the corresponding side. At least one axial end face of the cylinder liner (20) is also provided with a connecting hole (26), and the connecting hole (26) is connected to the exhaust cavity (25). The flange (50) opposite to the connecting hole (26) of the two flanges (50) is provided with a first exhaust channel (511), and the connecting hole (26) is connected to the first exhaust channel (511); the flange (50) on the side away from the exhaust port (22) of the two flanges (50) has a second exhaust channel (512), and the second exhaust channel (512) is connected to the variable volume cavity on the corresponding side.

21. The fluid machinery according to claim 17, 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, which is connected to the cylinder liner (20) and seals the exhaust chamber (25).

22. The fluid machinery according to any one of claims 17 to 21, characterized in that, The end of the radial intake hole (21) is the first compression intake port, the end of the intake passage (54) is the second compression intake port, and the exhaust port (22) on the cylinder liner (20) is the compression exhaust port. When the slider (40) located on the side corresponding to the radial air intake hole (21) is in the air intake position, the first compression air intake port is connected to the corresponding variable volume cavity. When the slider (40) located on the side corresponding to the radial air intake hole (21) is in the exhaust position, the corresponding variable volume cavity is connected to the compression exhaust port on the corresponding side. When the slider (40) located on the side corresponding to the intake channel (54) is in the intake position, the second compression intake port is connected to the corresponding variable volume cavity. When the slider (40) located on the side corresponding to the intake channel (54) is in the exhaust position, the corresponding variable volume cavity is connected to the corresponding compression exhaust port.

23. The fluid machinery according to claim 22, characterized in that, The fluid machinery is a compressor.

24. The fluid machinery according to any one of claims 17 to 21, characterized in that, The end of the radial intake hole (21) is the first expansion exhaust port, the end of the intake passage (54) is the second expansion exhaust port, and the exhaust port (22) on the cylinder liner (20) is the expansion intake port. When the slider (40) located on the side corresponding to the radial air intake hole (21) is in the air intake position, the first expansion exhaust port is connected to the corresponding variable volume cavity. When the slider (40) located on the side corresponding to the radial air intake hole (21) is in the exhaust position, the corresponding variable volume cavity is connected to the expansion air intake port on the corresponding side. When the slider (40) located on the side corresponding to the air intake channel (54) is in the air intake position, the second expansion exhaust port is connected to the corresponding variable volume cavity. When the slider (40) located on the side corresponding to the air intake channel (54) is in the exhaust position, the corresponding variable volume cavity is connected to the expansion air intake port on the corresponding side.

25. The fluid machinery according to claim 24, characterized in that, The fluid machinery is an expander.

26. The fluid machinery according to claim 1, characterized in that, There is a phase difference of a first included angle A between the two eccentric portions (11), the eccentricity of the two eccentric portions (11) is equal, and there is a phase difference of a second included angle B between the extension directions of the two limiting channels (31), wherein the first included angle A is twice the second included angle B.

27. 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 26.

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