Fluid machine and heat exchange device

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, and a slider. The crankshaft has a first eccentric portion and a second eccentric portion along its axial direction. The crankshaft and cylinder liner are eccentrically positioned with a fixed eccentricity. The cross-groove structure is rotatably disposed within the cylinder liner. A first limiting channel and a second limiting channel of the cross-groove structure are sequentially arranged along the axial direction of the crankshaft, with the extension direction of the first and second limiting channels perpendicular to the axial direction of the crankshaft. The second eccentric portion is slidably disposed within the second limiting channel, forming a limiting cavity. The first eccentric portion extends into a through hole in the slider. The slider is slidably disposed within the first limiting channel, forming a variable volume cavity. The rotation of the crankshaft drives the slider to reciprocate within the first limiting channel while interacting with the cross-groove structure, causing the cross-groove structure and the slider to rotate within the cylinder liner. This invention solves the problems of low energy efficiency and high noise and vibration 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. 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 to solve the problems of low energy efficiency and high noise and vibration 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, and a slider, wherein the crankshaft has a first eccentric portion and a second eccentric portion arranged along its axial direction; the crankshaft and the cylinder liner are eccentrically arranged with a fixed eccentricity; the cross-groove structure is rotatably disposed within the cylinder liner, the cross-groove structure having a first limiting channel and a second limiting channel, the first limiting channel and the second limiting channel being sequentially arranged along the axial direction of the crankshaft, and the first limiting channel being located above the second limiting channel, the extending directions of the first limiting channel and the second limiting channel being perpendicular to the axial direction of the crankshaft; the second eccentric portion is slidably disposed within the second limiting channel and forms a limiting cavity, the limiting cavity being located in the sliding direction of the second eccentric portion; the slider has a through hole, the first eccentric portion extending into the through hole, the slider being slidably disposed within the first limiting channel and forming a variable volume cavity, the variable volume cavity being located in the sliding direction of the slider, the crankshaft rotating to drive the slider to reciprocate within the first limiting channel while interacting with the cross-groove structure, so that the cross-groove structure and the slider rotate within the cylinder liner.

[0007] Furthermore, the fluid machinery also includes an upper flange and a lower flange, which are respectively located at both ends of the cylinder liner. The end face of the second eccentric part facing the lower flange serves as a thrust surface so that the second eccentric part makes thrust contact with the lower flange.

[0008] Furthermore, the height of the first eccentric part in the axial direction of the crankshaft is greater than the height of the second eccentric part in the axial direction of the crankshaft.

[0009] Furthermore, the second limiting channel extends directly through the cross groove structure along its axial direction to the end face of the cross groove structure, so that one end of the cross groove structure is open. The end face of the cross groove structure without the open end is reserved with an opening for the crankshaft to extend out. The opening is concentrically set with the cross groove structure and is connected to the first limiting channel.

[0010] Furthermore, the height H1 of the second eccentric part in the axial direction of the crankshaft and the height H2 of the second limiting channel in the axial direction of the cross groove structure satisfy the condition: H2-H1>0.5mm, so that the height difference between the two forms a pressure relief channel, which is used to connect the two limiting cavities.

[0011] Furthermore, the crankshaft includes a shaft body, on which a first eccentric portion and a second eccentric portion are provided; the second eccentric portion includes an eccentric portion body and a limiting ring, wherein the eccentric portion body is integrally formed with the shaft body; the limiting ring is sleeved on the outer periphery of the eccentric portion body, and the limiting ring is detachably connected to the eccentric portion body.

[0012] Furthermore, the height H1 of the second eccentric portion in the axial direction of the crankshaft, the height H2 of the second limiting channel in the axial direction of the cross groove structure, and the height H3 of the limiting ring in the axial direction of the crankshaft satisfy the following: H2>H1>H3, and 0.5≤H3 / H2≤1, so that at least the height difference between the second eccentric portion and the second limiting channel forms a first pressure relief channel to connect the two limiting cavities through the first pressure relief channel, and the height difference between the limiting ring and the second limiting channel forms a second pressure relief channel to connect the two limiting cavities through the second pressure relief channel.

[0013] Furthermore, the height H1 of the second eccentric part in the axial direction of the crankshaft and the height H2 of the second limiting channel in the axial direction of the cross groove structure satisfy the following condition: 0.05≤H1 / H2<1.

[0014] Furthermore, the cross-groove structure has a central hole for connecting the first limiting channel and the second limiting channel. The diameter D1 of the second eccentric part and the diameter D3 of the central hole satisfy the following: the design range of D1-D3 is 0.1mm to 5mm.

[0015] Furthermore, the cross-groove structure has a central hole for connecting the first limiting channel and the second limiting channel. The diameter D5 of the crankshaft shaft portion located on the side of the second eccentric portion away from the first eccentric portion, the diameter D3 of the central hole, and the diameter D1 of the second eccentric portion satisfy the following: D5 + 2 × e + 2 × L3 = D1, D1 + 2L5 = D3, where e is the eccentricity of the first eccentric portion, L3 is the third reserved gap between the outer surface of the crankshaft shaft portion located on the side of the second eccentric portion away from the first eccentric portion and the outer surface of the proximal end of the second eccentric portion, and L5 is the fifth reserved gap between the second eccentric portion and the hole wall of the central hole when the second eccentric portion and the central hole are concentric.

[0016] Furthermore, the design range of the third reserved gap L3 is 0.05mm to 3mm.

[0017] Furthermore, the design range of the fifth reserved gap L5 is 0.05mm to 5mm.

[0018] Furthermore, there is a first reserved gap L1 between the outer peripheral surface of the slider and the channel wall of the first limiting channel, and the design range of the first reserved gap L1 is 0.008mm to 0.05mm.

[0019] Furthermore, there is a fourth reserved gap L4 between the outer peripheral surface of the second eccentric part and the channel wall of the second limiting channel, and the design range of the fourth reserved gap L4 is 0.008mm to 0.05mm.

[0020] Furthermore, in the direction perpendicular to the sliding direction of the limiting ring, there is a second reserved gap L2 between the outer surface of the limiting ring and the channel wall of the second limiting channel, and the design range of the second reserved gap L2 is 0.008mm to 0.05mm.

[0021] Furthermore, there is a fifth reserved gap L5 between the inner wall surface of the limiting ring and the outer peripheral surface of the eccentric part body, and the design range of the fifth reserved gap L5 is 0.008mm to 0.05mm.

[0022] Furthermore, the inner wall surface of the limiting ring is adapted to the outer peripheral surface of the eccentric part body.

[0023] Furthermore, there is a phase difference of a first included angle A between the first eccentric part and the second eccentric part, the eccentricity of the first eccentric part is equal to the eccentricity of the second eccentric part, and there is a phase difference of a second included angle B between the extension direction of the first limiting channel and the extension direction of the second limiting channel, wherein the first included angle A is twice the second included angle B.

[0024] Furthermore, the first eccentric part and the second eccentric part are arranged opposite each other at 180°.

[0025] 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.

[0026] By applying the technical solution of this invention, the cross-groove structure is configured with a first limiting channel and a second limiting channel. Simultaneously, a second eccentric portion is slidably disposed within the second limiting channel to form a limiting cavity, located in the sliding direction of the second eccentric portion. Furthermore, a slider is slidably disposed within the first limiting channel to form a variable volume cavity, located in the sliding direction of the slider. The crankshaft rotates to drive the slider to reciprocate within the first limiting channel while interacting with the cross-groove structure, causing the cross-groove structure and the slider to rotate within the cylinder liner. This avoids the dead point position of the fluid machinery, improves the motion reliability of the fluid machinery, and thus ensures the operational reliability of the heat exchange equipment.

[0027] 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 and vibration, thereby ensuring the working reliability of the heat exchange equipment. Attached Figure Description

[0028] 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:

[0029] Figure 1 A schematic diagram of the pump body assembly of a compressor according to Embodiment 1 of the present invention is shown;

[0030] Figure 2 It shows Figure 1 A cross-sectional view of the structure at point CC;

[0031] Figure 3 It shows Figure 1 Schematic diagram of the cross-sectional structure at DD in the diagram;

[0032] Figure 4 It shows Figure 1 A cross-sectional view of the pump body assembly.

[0033] Figure 5 It shows Figure 1 An exploded view of the pump body components;

[0034] Figure 6 It shows Figure 5 A schematic diagram of the crankshaft structure of the pump body assembly;

[0035] Figure 7 It shows Figure 5 A cross-sectional view of the cross-groove structure of the pump body assembly;

[0036] Figure 8 A schematic diagram of the limiting ring according to Embodiment 1 of the present invention is shown;

[0037] Figure 9 It shows Figure 1 A schematic diagram of the crankshaft and cross groove structure in the assembly state;

[0038] Figure 10 It shows Figure 1 A top-view structural diagram of the crankshaft shaft body and the second eccentric part.

[0039] Figure 11 It shows Figure 5 A schematic diagram of the slider of the pump body assembly in its sliding direction;

[0040] Figure 12 It shows Figure 5 A schematic diagram of the cross-groove structure of the pump body assembly in the sliding direction of the slider;

[0041] Figure 13 It shows Figure 8 A three-dimensional structural diagram of the limiting ring in the middle;

[0042] Figure 14 It shows Figure 13 Another structural diagram of the limiting ring in the middle;

[0043] Figure 15 A schematic diagram of the limiting ring according to Embodiment 2 of the present invention is shown;

[0044] Figure 16 A schematic diagram of the limiting ring according to Embodiment 3 of the present invention is shown;

[0045] Figure 17 A schematic diagram of the pump body assembly of a compressor according to Embodiment 2 of the present invention is shown;

[0046] Figure 18 It shows Figure 17 A cross-sectional structural diagram from the EE perspective.

[0047] The above figures include the following reference numerals:

[0048] 10. Crankshaft; 11. First eccentric part; 12. Second eccentric part; 121. Eccentric part body; 122. Limiting ring; 1221. Assembly hole; 13. Shaft body;

[0049] 20. Cylinder liner;

[0050] 30. Cross-groove structure; 31. First limiting channel; 311. Variable volume cavity; 32. Second limiting channel; 321. Limiting cavity; 33. Opening; 34. Center hole;

[0051] 40. Slider; 41. Through hole;

[0052] 50. Upper flange; 60. Lower flange. Detailed Implementation

[0053] 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.

[0054] It should be noted that the two limit channels of the twin-cylinder rotary piston compressor are arranged symmetrically at 180°, which can make the change of load torque more gradual, so the compressor vibration is very small. However, due to its own defects, the gas leakage loss of the above compressor is also very high. On the other hand, the gas leakage loss of the single-cylinder rotary piston compressor is smaller, but the torque peak is very large, and the compressor vibration is also relatively large.

[0055] In order to solve the problems of low energy efficiency and high noise and vibration of compressors in the prior art, the present invention provides a fluid machine and a heat exchange device, wherein the heat exchange device includes a fluid machine, and the fluid machine is the fluid machine described above and below.

[0056] Example 1

[0057] like Figures 1 to 16As shown, the fluid machinery includes a crankshaft 10, a cylinder liner 20, a cross-groove structure 30, and a slider 40. The crankshaft 10 has a first eccentric portion 11 and a second eccentric portion 12 arranged along its axial direction. The crankshaft 10 and the cylinder liner 20 are eccentrically positioned with a fixed eccentricity. The cross-groove structure 30 is rotatably disposed within the cylinder liner 20. The cross-groove structure 30 has a first limiting channel 31 and a second limiting channel 32, which are sequentially arranged along the axial direction of the crankshaft 10. The first limiting channel 31 is located above the second limiting channel 32, and the extension directions of the first limiting channel 31 and the second limiting channel 32 are... Perpendicular to the axial direction of the crankshaft 10, the second eccentric part 12 is slidably disposed in the second limiting channel 32 and forms a limiting cavity 321, which is located in the sliding direction of the second eccentric part 12; the slider 40 has a through hole 41, the first eccentric part 11 extends into the through hole 41, the slider 40 is slidably disposed in the first limiting channel 31 and forms a variable volume cavity 311, which 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 first 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.

[0058] By configuring the cross-groove structure 30 with a first limiting channel 31 and a second limiting channel 32, and simultaneously sliding the second eccentric part 12 within the second limiting channel 32 to form a limiting cavity 321, the limiting cavity 321 is located in the sliding direction of the second eccentric part 12. In addition, the slider 40 is slidably configured within the first limiting channel 31 to 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 reciprocate within the first limiting channel 31 while interacting with the cross-groove structure 30, so that the cross-groove structure 30 and the slider 40 rotate within the cylinder liner 20. In this way, the dead point position of the fluid machinery is avoided, the motion reliability of the fluid machinery is improved, and the working reliability of the heat exchange equipment is ensured.

[0059] 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 and vibration, thereby ensuring the working reliability of the heat exchange equipment.

[0060] like Figures 13 to 16 As shown, since the limiting ring 122 does not participate in the compressor's intake and exhaust process, as long as its two sides can contact the channel wall of the second limiting channel 32 and drive the cross groove structure 30 to rotate, the mounting hole 1221 of the limiting ring 122 is circular, and the outer contour of the limiting ring 122 can be a circle, a semi-circle, a square, or other shapes.

[0061] It should be noted that in this application, when the first eccentric part 11 rotates to zero torque, the second eccentric part 12, which is symmetrical to it, can provide force to drive the compressor to rotate, and the problem of zero torque is compensated by the principle of double eccentric parts.

[0062] It should be noted that, in this application, if Figure 2 As shown, unlike rotary compressors, the compressor in this application features an eccentric design between the cylinder liner 20 and the crankshaft 10. During compressor operation, the crankshaft 10 drives the slider 40 and the cross-groove structure 30 to rotate within the cylinder liner 20. The cross-groove structure 30 and the crankshaft 10 rotate around their respective centers, while the slider 40 reciprocates simultaneously relative to both the cross-groove structure 30 and the crankshaft 10. This reciprocating motion of the slider 40 relative to the cross-groove structure 30 enables the periodic expansion and contraction of the variable volume cavity 311. Meanwhile, the circular motion of the cross-groove structure 30 relative to the cylinder liner 20 connects the variable volume cavity 311 to both the intake and exhaust channels. These two combined motions realize the compressor's intake, compression, and exhaust processes. Because variable volume cavities 311 exist at both ends of the slider 40, this structure can also be considered a single-cylinder dual-compression structure.

[0063] Due to the unique characteristics of a single-cylinder dual-compression structure, the torque becomes zero when it rotates to a certain angle, preventing the compressor from starting at that angle. Therefore, this application primarily addresses this problem and provides several new structural solutions.

[0064] like Figure 3 As shown, the second limiting channel 32 and the second eccentric part 12 cooperate to form a limiting cavity 321, which may periodically increase or decrease in size. However, the limiting cavity 321 does not have a matching intake or exhaust channel, so it does not participate in compression.

[0065] It should be noted that in this application, fluid machinery includes compressors. This application takes compressors as an example, and the main improvement is in the pump body assembly of the compressor.

[0066] like Figure 1 , Figure 4 , Figure 5 As shown, the fluid machinery also includes an upper flange 50 and a lower flange 60, which are respectively disposed at both ends of the cylinder liner 20. The end face of the second eccentric part 12 facing the lower flange 60 serves as a thrust surface so that the second eccentric part 12 makes thrust contact with the lower flange 60.

[0067] It should be noted that, in this application, considering that the second limiting channel 32 directly penetrates the end face of the cross groove structure 30 along its axial direction, making the end of the cross groove structure 30 with the second limiting channel 32 open, the height of the first limiting channel 31 in the axial direction of the cross groove structure 30 is set higher than the height of the second limiting channel 32 in the axial direction of the cross groove structure 30 to prevent leakage. Figure 16 As shown, the height of the first eccentric portion 11 in the axial direction of the crankshaft 10 is greater than the height of the second eccentric portion 12 in the axial direction of the crankshaft 10. This ensures the adaptability of the slider 40 when it is slidably disposed within the first limiting channel 31, and also ensures the adaptability of the second eccentric portion 12 when it is slidably disposed within the second limiting channel 32.

[0068] It should be noted that in this application, a certain amount of refrigerant oil is typically added inside the compressor to dissipate heat and lubricate the pump assembly. The refrigerant oil level usually overflows the cylinder liner 20, and the central oil hole of the crankshaft 10 continuously supplies oil to the various friction pairs of the pump assembly. Therefore, the limiting cavity 321 is often full of oil. Since oil is incompressible and the gaps between the friction pairs are very small, oil is difficult to transfer. This increases the rotational resistance of the second eccentric part 12, thereby increasing the compressor's power consumption.

[0069] like Figure 6 and Figure 7 As shown, the height H1 of the second eccentric portion 12 in the axial direction of the crankshaft 10 and the height H2 of the second limiting channel 32 in the axial direction of the cross groove structure 30 satisfy the condition: H2-H1>0.5mm, so that the height difference between the two forms a pressure relief channel, which is used to connect the two limiting cavities 321. In this way, when the volume of one of the limiting cavities 321 decreases, the refrigerant oil flows through the gap (i.e., the pressure relief channel) between the end face of the second eccentric portion 12 and the end face of the cross groove structure 30 to the other limiting cavity 321 with a larger volume, ensuring that the two limiting cavities 321 can be effectively connected through the pressure relief channel, thereby ensuring the reliability of the connection between the two limiting cavities 321.

[0070] like Figures 4 to 6 As shown, the crankshaft 10 includes a shaft body 13, on which a first eccentric portion 11 and a second eccentric portion 12 are provided; the second eccentric portion 12 includes an eccentric portion body 121 and a limiting ring 122, wherein the eccentric portion body 121 is integrally formed with the shaft body 13; the limiting ring 122 is sleeved on the outer periphery of the eccentric portion body 121, and the limiting ring 122 is detachably connected to the eccentric portion body 121.

[0071] like Figures 6 to 8As shown, the height H1 of the second eccentric portion 12 in the axial direction of the crankshaft 10, the height H2 of the second limiting channel 32 in the axial direction of the cross groove structure 30, and the height H3 of the limiting ring 122 in the axial direction of the crankshaft 10 satisfy the following: H2>H1>H3, and 0.5≤H3 / H2≤1. This ensures that the height difference between at least the second eccentric portion 12 and the second limiting channel 32 forms a first pressure relief channel, connecting the two limiting cavities 321 through the first pressure relief channel. Furthermore, the height difference between the limiting ring 122 and the second limiting channel 32 forms a second pressure relief channel, connecting the two limiting cavities 321 through the second pressure relief channel. This ensures that the two limiting cavities 321 can be effectively connected through the first pressure relief channel and / or the second pressure relief channel.

[0072] like Figure 5 and Figure 7 As shown, the second limiting channel 32 extends directly through the end face of the cross groove structure 30 along its axial direction, making one end of the cross groove structure 30 open. The end face of the non-open end of the cross groove structure 30 has a pre-drilled opening 33 for the crankshaft 10 to extend from. The opening 33 is concentrically arranged with the cross groove structure 30 and communicates with the first limiting channel 31. This makes the cross groove structure 30 in this application a semi-closed structure. Furthermore, the opening 33 ensures the feasibility of assembling the crankshaft 10 with the cross groove structure 30.

[0073] like Figure 6 and Figure 7 As shown, the height H1 of the second eccentric part 12 in the axial direction of the crankshaft 10 and the height H2 of the second limiting channel 32 in the axial direction of the cross groove structure 30 satisfy the following condition: 0.05≤H1 / H2<1.

[0074] like Figure 6 and Figure 7 As shown, the cross-groove structure 30 has a central hole 34, which connects the first limiting channel 31 and the second limiting channel 32. The diameter D1 of the second eccentric portion 12 and the diameter D3 of the central hole 34 satisfy the following: the design range of D1-D3 is 0.1mm to 5mm. This ensures the feasibility of assembly between the cross-groove structure 30 and the crankshaft 10.

[0075] It should be noted that, in this application, in order to ensure the assembly feasibility between the crankshaft 10 and the cross-groove structure 30, such as Figure 6 and Figure 7As shown, the cross groove structure 30 has a central hole 34, which is used to connect the first limiting channel 31 and the second limiting channel 32. The diameter D5 of the shaft portion of the crankshaft 10 located on the side of the second eccentric portion 12 away from the first eccentric portion 11, the diameter D3 of the central hole 34, and the diameter D1 of the second eccentric portion 12 satisfy the following: D5 + 2 × e + 2 × L3 = D1, D1 + 2L5 = D3, where e is the eccentricity of the first eccentric portion 11, L3 is the third reserved gap between the outer surface of the shaft portion of the crankshaft 10 located on the side of the second eccentric portion 12 away from the first eccentric portion 11 and the outer surface of the proximal end of the second eccentric portion 12, and L5 is the fifth reserved gap between the second eccentric portion 12 and the hole wall of the central hole 34 when the second eccentric portion 12 and the central hole 34 are concentric.

[0076] Preferably, the design range of the third reserved gap L3 is 0.05mm to 3mm.

[0077] Preferably, the design range of the fifth reserved gap L5 is 0.05mm to 5mm.

[0078] It should be noted that in this application, there is a first reserved gap L1 between the outer peripheral surface of the slider 40 and the channel wall of the first limiting channel 31, and the design range of the first reserved gap L1 is 0.008mm to 0.05mm. This ensures the feasibility of assembly between the slider 40 and the cross groove structure 30, and ensures that there is no leakage between the slider 40 and the first limiting channel 31.

[0079] Furthermore, in a direction perpendicular to the sliding direction of the limiting ring 122, there is a second reserved gap L2 between the outer surface of the limiting ring 122 and the channel wall of the second limiting channel 32, and the design range of the second reserved gap L2 is 0.008mm to 0.05mm. This ensures the assembly reliability between the limiting ring 122 and the cross groove structure 30.

[0080] It should be noted that in this application, there is a fifth reserved gap L5 between the inner wall surface of the limiting ring 122 and the outer peripheral surface of the eccentric body 121, and the design range of the fifth reserved gap L5 is 0.008mm to 0.05mm. This ensures convenient assembly between the two.

[0081] Preferably, the inner wall surface of the limiting ring 122 is adapted to the outer peripheral surface of the eccentric body 121. This ensures that after assembly, the gap between the two can meet the design range as much as possible.

[0082] It should be noted that in this application, there is a phase difference of a first included angle A between the first eccentric part 11 and the second eccentric part 12, the eccentricity of the first eccentric part 11 is equal to the eccentricity of the second eccentric part 12, and there is a phase difference of a second included angle B between the extension direction of the first limiting channel 31 and the extension direction of the second limiting channel 32, wherein the first included angle A is twice the second included angle B.

[0083] Preferably, the first eccentric portion 11 and the second eccentric portion 12 are arranged opposite each other at 180°.

[0084] like Figure 1 , Figure 3 As shown, the upper flange 50 and the lower flange 60 are respectively located at both ends of the cylinder liner 20 along the axial direction.

[0085] Example 2

[0086] It should be noted that the difference between this embodiment and Embodiment 1 is that, as Figure 17 and Figure 18 As shown, the second eccentric part 12 is an integral structure, eliminating the limiting ring, which helps to reduce the number of parts in the pump body assembly. The diameter of the second eccentric part 12 is increased to ensure that the outer peripheral surface of the second eccentric part 12 can effectively contact the channel wall of the second limiting channel 32, so that the second eccentric part 12 can drive the cross groove structure 30 to rotate.

[0087] It should be noted that in this embodiment, there is a fourth reserved gap L4 between the outer peripheral surface of the second eccentric portion 12 and the channel wall of the second limiting channel 32, and the design range of the fourth reserved gap L4 is 0.008mm to 0.05mm. This ensures the assembly feasibility between the crankshaft 10 and the cross groove structure 30.

[0088] 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.

[0089] 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.

[0090] 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.

[0091] 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.

[0092] 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.

[0093] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A fluid machine characterized by, include: A crankshaft (10) having a first eccentric portion (11) and a second eccentric portion (12) along its axial direction; Cylinder liner (20), the crankshaft (10) and the cylinder liner (20) are eccentrically arranged and the eccentricity is fixed; A cross-groove structure (30) is rotatably disposed within the cylinder liner (20). The cross-groove structure (30) has a first limiting channel (31) and a second limiting channel (32). The first limiting channel (31) and the second limiting channel (32) are sequentially arranged along the axial direction of the crankshaft (10), and the first limiting channel (31) is located above the second limiting channel (32). The extending directions of the first limiting channel (31) and the second limiting channel (32) are perpendicular to the axial direction of the crankshaft (10). The second eccentric portion (12) is slidably disposed within the second limiting channel (32) and forms a limiting cavity (321). The limiting cavity (321) is located in the sliding direction of the second eccentric portion (12). The slider (40) has a through hole (41), the first eccentric part (11) extends into the through hole (41), the slider (40) is slidably disposed in the first limiting channel (31) and forms 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 first 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).

2. The fluid machine of claim 1, wherein, The fluid machinery also includes: The upper flange (50) and the lower flange (60) are respectively disposed at both ends of the cylinder liner (20). The end face of the second eccentric part (12) facing the lower flange (60) serves as a thrust surface so that the second eccentric part (12) makes thrust contact with the lower flange (60).

3. The fluid machine of claim 1, wherein, The height of the first eccentric part (11) in the axial direction of the crankshaft (10) is greater than the height of the second eccentric part (12) in the axial direction of the crankshaft (10).

4. The fluid machine of claim 1, wherein, The second limiting channel (32) extends directly through the cross groove structure (30) along its axial direction to the end face of the cross groove structure (30), so that one end of the cross groove structure (30) is open. The end face of the cross groove structure (30) without the open end is reserved with an opening (33) for the crankshaft (10) to extend out. The opening (33) is concentrically arranged with the cross groove structure (30) and the opening (33) is connected to the first limiting channel (31).

5. The fluid machine of claim 1, wherein, The second eccentric part (12) at a height H1 in the axial direction of the crankshaft (10) and the second limiting channel (32) at a height H2 in the axial direction of the cross groove structure (30) satisfy: H2-H1>0.5mm, so that the height difference between the two forms a pressure relief channel, which is used to connect the two limiting cavities (321).

6. The fluid machinery according to claim 1, characterized in that, The crankshaft (10) includes: Shaft (13), on which the first eccentric part (11) and the second eccentric part (12) are provided; The second eccentric portion (12) includes: An eccentric body (121) is integrally formed with the shaft (13); A limiting ring (122) is sleeved on the outer periphery of the eccentric part body (121), and the limiting ring (122) is detachably connected to the eccentric part body (121).

7. The fluid machine of claim 6, wherein, The height H1 of the second eccentric portion (12) in the axial direction of the crankshaft (10), the height H2 of the second limiting channel (32) in the axial direction of the cross groove structure (30), and the height H3 of the limiting ring (122) in the axial direction of the crankshaft (10) satisfy: H2>H1>H3, and 0.5≤H3 / H2≤1, so that at least the height difference between the second eccentric portion (12) and the second limiting channel (32) forms a first pressure relief channel to connect the two limiting cavities (321) through the first pressure relief channel, and the height difference between the limiting ring (122) and the second limiting channel (32) forms a second pressure relief channel to connect the two limiting cavities (321) through the second pressure relief channel.

8. The fluid machine of claim 6, wherein, The second eccentric part (12) at a height H1 in the axial direction of the crankshaft (10) and the second limiting channel (32) at a height H2 in the axial direction of the cross groove structure (30) satisfy the following condition: 0.05 ≤ H1 / H2 < 1.

9. The fluid machine of claim 6, wherein, The cross groove structure (30) has a central hole (34) for connecting the first limiting channel (31) and the second limiting channel (32). The diameter D1 of the second eccentric part (12) and the hole diameter D3 of the central hole (34) satisfy the following: 0.1mm≤D1-D3≤5mm.

10. The fluid machinery according to claim 6, characterized in that, The cross groove structure (30) has a central hole (34) for connecting the first limiting channel (31) and the second limiting channel (32). The diameter D5 of the shaft portion of the crankshaft (10) located on the side of the second eccentric portion (12) away from the first eccentric portion (11), the diameter D3 of the central hole (34), and the diameter D1 of the second eccentric portion (12) satisfy the following: D5 + 2 × e + 2 × L3 = D1, D1 + 2L5 =D3, where e is the eccentricity of the first eccentric part (11), L3 is the third reserved gap between the outer surface of the shaft portion of the crankshaft (10) located on the side of the second eccentric part (12) away from the first eccentric part (11) and the outer surface of the proximal end of the second eccentric part (12), and L5 is the fifth reserved gap between the second eccentric part (12) and the hole wall surface of the center hole (34) when the second eccentric part (12) is concentric with the center hole (34).

11. The fluid machinery according to claim 10, characterized in that, The design range of the third reserved gap L3 is 0.05mm to 3mm.

12. The fluid machinery according to claim 10, characterized in that, The design range of the fifth reserved gap L5 is 0.05mm to 5mm.

13. The fluid machinery according to claim 6, characterized in that, There is a first reserved gap L1 between the outer peripheral surface of the slider (40) and the channel wall of the first limiting channel (31), and the design range of the first reserved gap L1 is 0.008mm~0.05mm.

14. The fluid machinery according to claim 6, characterized in that, The outer peripheral surface of the second eccentric part (12) and the channel wall of the second limiting channel (32) have a fourth reserved gap L4, and the design range of the fourth reserved gap L4 is 0.008mm~0.05mm.

15. The fluid machinery according to claim 6, characterized in that, In a direction perpendicular to the sliding direction of the limiting ring (122), there is a second reserved gap L2 between the outer surface of the limiting ring (122) and the channel wall of the second limiting channel (32), and the design range of the second reserved gap L2 is 0.008mm~0.05mm.

16. The fluid machinery according to claim 6, characterized in that, The inner wall of the limiting ring (122) and the outer peripheral surface of the eccentric body (121) have a fifth reserved gap L5, and the design range of the fifth reserved gap L5 is 0.008mm~0.05mm.

17. The fluid machinery according to any one of claims 6 to 16, characterized in that, The inner wall surface of the limiting ring (122) is adapted to the outer peripheral surface of the eccentric body (121).

18. The fluid machinery according to claim 1, characterized in that, There is a phase difference of a first included angle A between the first eccentric part (11) and the second eccentric part (12), the eccentricity of the first eccentric part (11) is equal to the eccentricity of the second eccentric part (12), and there is a phase difference of a second included angle B between the extension direction of the first limiting channel (31) and the extension direction of the second limiting channel (32), wherein the first included angle A is twice the second included angle B.

19. The fluid machinery according to claim 18, characterized in that, The first eccentric part (11) and the second eccentric part (12) are arranged opposite each other at 180°.

20. A heat exchange device, characterized in that, Includes fluid machinery, wherein the fluid machinery is the fluid machinery according to any one of claims 1 to 19.

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