Fluid machine and heat exchange device

Abstract

The application provides a fluid machine and a heat exchange device. The fluid machine comprises a crankshaft, a cylinder sleeve, a cross groove structure and a slider. The crankshaft has a first eccentric part and a second eccentric part. The crankshaft is eccentrically arranged with the cylinder sleeve and the eccentric distance is fixed. The cross groove structure is rotatably arranged in the cylinder sleeve. The first limiting channel and the second limiting channel of the cross groove structure are sequentially arranged along the axial direction of the crankshaft. The extension direction of the first limiting channel and the second limiting channel is perpendicular to the axial direction of the crankshaft. The first eccentric part is slidingly arranged in the first limiting channel and forms a limiting cavity. The slider has a through hole. The second eccentric part extends into the through hole. The slider is slidingly arranged in the second limiting channel and forms a variable volume cavity. The variable volume cavity is located in the sliding direction of the slider. The application solves the problem of low energy efficiency of the compressor in the prior art.

Description

Technical Field

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

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

[0003] In accordance with national energy conservation and environmental protection policies and consumer demands for air conditioning comfort, the air conditioning industry has been pursuing high efficiency and low noise. The compressor, as the heart of the air conditioner, directly impacts its energy efficiency and noise level. 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 problem of low energy efficiency 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 is provided with a first eccentric portion and a second eccentric portion along its axial direction; the crankshaft and the cylinder liner are eccentrically disposed with a fixed eccentric distance; 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 disposed along the axial direction of the crankshaft, the extending direction of the first limiting channel and the second limiting channel being perpendicular to the axial direction of the crankshaft; the first eccentric portion is slidably disposed within the first limiting channel and forms a limiting cavity, the limiting cavity being located in the sliding direction of the first eccentric portion; the slider has a through hole, the second eccentric portion extending into the through hole, the slider being slidably disposed within the second limiting channel and forms 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 second limiting channel while interacting with the cross-groove structure, thereby causing the cross-groove structure and the slider to rotate within the cylinder liner.

[0007] Furthermore, the end face of the first eccentric portion facing the cross groove structure serves as a thrust surface, so that the first eccentric portion makes thrust contact with the cross groove structure.

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

[0009] Furthermore, the height of the first limiting channel in the axial direction of the cross groove structure is less than the height of the second limiting channel in the axial direction of the cross groove structure.

[0010] Furthermore, the fluid machinery also includes a flange and a lower flange, with the upper flange and lower flange respectively located at the axial ends of the cylinder liner. The end face of the first eccentric part facing the upper flange serves as a thrust surface, so that the first eccentric part makes thrust contact with the upper flange.

[0011] Furthermore, the first 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 second limiting channel.

[0012] Furthermore, the cross-groove structure has a central hole for connecting the first limiting channel and the second limiting channel. The diameters D1 of the first eccentric part, D2 of the second eccentric part, and D3 of the central hole satisfy the following relationship: D1 > D3 > D2.

[0013] Furthermore, the cross-groove structure has a central hole for connecting the first limiting channel and the second limiting channel. The diameter D4 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 D2 of the second eccentric portion satisfy the following: D4 + 2 × e + 2 × L1 = D2, D2 + 2L5 = D3, where e is the eccentricity of the first eccentric portion, L1 is the first 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 is concentric with the central hole.

[0014] Furthermore, the design range of the first reserved gap L1 is 0.05mm to 3mm.

[0015] Furthermore, the design range of the fifth reserved gap L5 is 0.05mm to 5mm.

[0016] Furthermore, the height H2 of the first limiting channel in the axial direction of the cross groove structure and the height H3 of the first eccentric part in the axial direction of the crankshaft satisfy the following condition: 0.05≤H3 / H2<1.

[0017] Furthermore, there is a second reserved gap L2 between the outer peripheral surface of the first eccentric part and the channel wall of the first limiting channel, and the design range of the second reserved gap L2 is 0.008mm to 0.05mm.

[0018] Furthermore, the projection of the slider in its sliding direction is circular, the projection of the second limiting channel in the sliding direction of the slider is circular, and there is a third reserved gap L3 between the outer peripheral surface of the slider and the channel wall of the second limiting channel, and the design range of the third reserved gap L3 is 0.008mm~0.05mm.

[0019] 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 upper flange facing the cylinder liner is provided with a pressure relief ring groove, which is used to connect the two limiting cavities.

[0020] Furthermore, the pressure relief ring groove is eccentrically positioned.

[0021] Furthermore, the outer diameter D10 of the pressure relief ring groove and the outer diameter D8 of the cross groove structure satisfy the following condition: 0.1≤D10 / D8≤0.9.

[0022] Furthermore, the cross-section of the pressure relief ring groove is one of the following: circular, square, or elliptical.

[0023] Furthermore, the height H2 of the first limiting channel in the axial direction of the cross groove structure and the height H3 of the first eccentric part in the axial direction of the crankshaft satisfy the following: the design range of H2-H3 is 0.5mm to 5mm, so that the height difference between the first limiting channel and the first eccentric part forms a pressure relief channel, and the pressure relief channel is used to communicate with the two limiting cavities.

[0024] Furthermore, in the sliding direction of the first eccentric part, a channel pressure relief groove is provided on the channel wall of the first limiting channel. The channel pressure relief groove passes through the two radial sides of the cross groove structure and is used to connect the two limiting cavities.

[0025] Furthermore, two crankshaft pressure relief grooves are formed on the end face of the first eccentric part away from the second eccentric part. The two crankshaft pressure relief grooves are respectively located on both sides of the line connecting the proximal and distal ends of the first eccentric part. Two connecting notches are formed on the outer peripheral surface of the first eccentric part. The two connecting notches are respectively located on both sides of the line connecting the proximal and distal ends of the first eccentric part, and each crankshaft pressure relief groove is connected to the corresponding limiting cavity through the connecting notch.

[0026] Furthermore, the two crankshaft relief grooves have a 180° phase difference; the two connecting notches have a 180° phase difference.

[0027] 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.

[0028] Furthermore, the first eccentric part and the second eccentric part are arranged opposite each other at 180°.

[0029] 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.

[0030] By applying the technical solution of this invention, a single-cylinder dual-compression structure is proposed. This structure is achieved by configuring the cross-groove structure with a first limiting channel and a second limiting channel. A first eccentric portion is slidably disposed within the first limiting channel to form a limiting cavity, located in the sliding direction of the first eccentric portion. A slider is slidably disposed within the second limiting channel to form a variable-volume cavity, located in the sliding direction of the slider. This allows the crankshaft to rotate, driving the slider to reciprocate within the second limiting channel while interacting with the cross-groove structure. This enables the cross-groove structure and the slider to rotate within the cylinder liner, avoiding dead spots in the fluid machinery, improving the motion reliability of the fluid machinery, and thus ensuring the operational reliability of the heat exchange equipment.

[0031] Furthermore, since the fluid machinery provided in this application can operate stably, that is, it ensures the high energy efficiency of the compressor, thereby ensuring the operational reliability of the heat exchange equipment. Attached Figure Description

[0032] 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:

[0033] Figure 1 A schematic diagram of the pump body assembly of a compressor according to an optional embodiment of the present invention is shown;

[0034] Figure 2 It shows Figure 1 An exploded view of the pump body components;

[0035] Figure 3 It shows Figure 1 A partial structural diagram of the pump body assembly;

[0036] Figure 4 It shows Figure 2 A schematic diagram of the crankshaft and cross groove structure of the pump body assembly in the assembled state;

[0037] Figure 5 It shows Figure 4 Another structural diagram of the pump body assembly;

[0038] Figure 6 It shows Figure 1 A schematic diagram of the pump body assembly in the diagram;

[0039] Figure 7 It shows Figure 6 A magnified structural diagram of the CC section;

[0040] Figure 8 It shows Figure 6 A magnified structural diagram of the DD section;

[0041] Figure 9 It shows Figure 2 A schematic diagram of the crankshaft structure of the pump body assembly;

[0042] Figure 10 It shows Figure 2 A schematic diagram of the cross-groove structure of the pump body assembly;

[0043] Figure 11 It shows Figure 4 The cross groove structure and the structural diagram of the crankshaft in the assembly state from a top view.

[0044] Figure 12 It shows Figure 2 A schematic diagram of the cross-groove structure of the pump body assembly;

[0045] Figure 13 It shows Figure 2 A schematic diagram of the upper flange of the pump body assembly;

[0046] Figure 14 It shows Figure 2 A schematic diagram of the upper flange and cross groove structure of the pump body assembly in the assembled state;

[0047] Figure 15 A partial structural schematic diagram of the pump body assembly of a compressor according to an optional embodiment of the present invention is shown, in which the lower flange is omitted;

[0048] Figure 16 It shows Figure 15 A schematic diagram of the structure of the upper flange of the pump body assembly in the first embodiment;

[0049] Figure 17 It shows Figure 15 A schematic diagram of the structure of the upper flange of the pump body assembly in the second embodiment;

[0050] Figure 18 It shows Figure 15 A schematic diagram of the structure of the upper flange of the pump body assembly in the third embodiment;

[0051] Figure 19 A partial structural schematic diagram of the pump body assembly of a compressor according to an optional embodiment of the present invention is shown, in which the lower flange is omitted;

[0052] Figure 20 It shows Figure 19 A schematic diagram of the crankshaft and cross groove structure of the pump body assembly in the assembled state;

[0053] Figure 21 A schematic diagram of the cross-groove structure of a pump body assembly according to an optional embodiment of the present invention is shown;

[0054] Figure 22 A schematic diagram of the crankshaft of a pump body assembly according to an alternative embodiment of the present invention is shown;

[0055] Figure 23 It shows Figure 1 A top-view structural diagram of the crankshaft shaft body and the second eccentric part.

[0056] The above figures include the following reference numerals:

[0057] 10. Crankshaft; 11. First eccentric part; 111. Crankshaft pressure relief groove; 112. Connecting notch; 12. Second eccentric part;

[0058] 20. Cylinder liner;

[0059] 30. Cross-groove structure; 31. First limiting channel; 311. Limiting cavity; 312. Channel pressure relief groove; 32. Second limiting channel; 321. Variable volume cavity; 33. Opening; 34. Center hole;

[0060] 40. Slider; 41. Through hole;

[0061] 60. Upper flange; 61. Pressure relief ring groove; 70. Lower flange; 80. Pressure relief channel. Detailed Implementation

[0062] 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.

[0063] To address the problem of low energy efficiency 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.

[0064] like Figures 1 to 23As 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 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 first eccentric part 11 is slidably disposed in the first limiting channel 31 and forms a limiting cavity 311, the limiting cavity 311 being located in the sliding direction of the first eccentric part 11; the slider 40 has a through hole 41, the second eccentric part 12 extends into the through hole 41, the slider 40 is slidably disposed in the second limiting channel 32 and forms a variable volume cavity 321, the variable volume cavity 321 being 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 second limiting channel 32 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.

[0065] This application proposes a single-cylinder dual-compression structure. By configuring the cross-groove structure 30 with a first limiting channel 31 and a second limiting channel 32, and correspondingly sliding the first eccentric part 11 within the first limiting channel 31 to form a limiting cavity 311, the limiting cavity 311 is located in the sliding direction of the first eccentric part 11, and the slider 40 is slidably configured within the second limiting channel 32 to form a variable volume cavity 321, the variable volume cavity 321 is located in the sliding direction of the slider 40. This allows the crankshaft 10 to rotate, driving the slider 40 to reciprocate within the second limiting channel 32 while interacting with the cross-groove structure 30. This causes the cross-groove structure 30 and the slider 40 to rotate within the cylinder liner 20, avoiding the dead point position of the fluid machinery, improving the motion reliability of the fluid machinery, and thus ensuring the working reliability of the heat exchange equipment.

[0066] Furthermore, since the fluid machinery provided in this application can operate stably, that is, it ensures the high energy efficiency of the compressor, thereby ensuring the operational reliability of the heat exchange equipment.

[0067] It should be noted that this application proposes a novel single-cylinder dual-compression compressor. Based on the cross-slot structure with two limiting channels and the mechanism principle of double slider, the compressor can avoid the dead point problem of the compressor in principle, and at the same time has the characteristics of high energy efficiency, simple assembly and good parts manufacturability. The following uses the compressor as an example to specifically introduce the compressor based on the cross-slot structure 30 with the first limiting channel 31 and the second limiting channel 32 and the slider 40.

[0068] It should be noted that in this application, the end face of the first eccentric portion 11 facing the cross groove structure 30 serves as a thrust surface, so that the first eccentric portion 11 makes thrust contact with the cross groove structure 30. This helps to reduce the wear on the end face of the upper flange 60, thereby improving the reliability of the compressor.

[0069] like Figure 1 As shown, the fluid machinery also includes an upper flange 60 and a lower flange 70, which are respectively disposed at both ends of the cylinder liner 20.

[0070] like Figures 2 to 5 As shown, the first limiting channel 31 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 through. The opening 33 is concentrically arranged with the cross groove structure 30 and communicates with the second limiting channel 32. Thus, the opening 33 ensures that the shaft portion of the crankshaft 10 can pass through, ensuring the feasibility of assembly between the two.

[0071] It should be noted that, in this application, considering that the first limiting channel 31 directly penetrates the end face of the cross groove structure 30 along its axial direction, thus making one end of the cross groove structure 30 open, the height of the first limiting channel 31 in the axial direction of the cross groove structure 30 is less than the height of the second limiting channel 32 in the axial direction of the cross groove structure 30. Figure 1 , Figure 2 , Figure 4 As shown, the height of the first eccentric part 11 in the axial direction of the crankshaft 10 is less than the height of the second eccentric part 12 in the axial direction of the crankshaft 10.

[0072] It should be noted that, in this application, in order to meet the assembly requirements of the compressor's pump body assembly and the fact that the crankshaft's thrust face has a certain bearing area, such as... Figure 9 and Figure 10 As 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 D1 of the first eccentric part 11, the diameter D2 of the second eccentric part 12, and the diameter D3 of the central hole 34 satisfy the following relationship: D1 > D3 > D2.

[0073] like Figures 9 to 11As 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 D4 of the crankshaft 10 shaft portion 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 D2 of the second eccentric portion 12 satisfy the following: D4 + 2 × e + 2 × L1 = D2, D2 + 2L5 = D3, where e is the eccentricity of the first eccentric portion 11, L1 is the first reserved gap between the outer surface of the crankshaft 10 shaft portion 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 is concentric with the central hole 34. This ensures the assembly feasibility of the pump body assembly.

[0074] Optionally, the design range of the first reserved gap L1 is 0.05mm to 3mm. This ensures that the assembly of the compressor's pump body assembly is simple and convenient.

[0075] Optionally, the design range of the fifth reserved gap L5 is 0.05mm to 5mm.

[0076] like Figure 9 and Figure 12 As shown, the height H2 of the first limiting channel 31 in the axial direction of the cross groove structure 30 and the height H3 of the first eccentric part 11 in the axial direction of the crankshaft 10 satisfy the following condition: 0.05 ≤ H3 / H2 < 1. This reduces compressor friction and compression power consumption, improving compressor performance and reliability.

[0077] Optionally, a second reserved gap L2 is provided between the outer peripheral surface of the first eccentric portion 11 and the channel wall of the first limiting channel 31, and the design range of the second reserved gap L2 is 0.008mm to 0.05mm. In this way, the frictional power consumption between the first eccentric portion 11 of the crankshaft 10 and the cross groove structure 30 is reduced, abnormal wear is avoided, and the performance and reliability of the compressor are improved.

[0078] Optionally, the projection of the slider 40 in its sliding direction is circular, the projection of the second limiting channel 32 in the sliding direction of the slider 40 is circular, and there is a third reserved gap L3 between the outer peripheral surface of the slider 40 and the channel wall of the second limiting channel 32, with the design range of the third reserved gap L3 being 0.008mm to 0.05mm. This reduces leakage between the slider 40 and the cross-groove structure 30, improving the compressor's cooling capacity and performance.

[0079] like Figures 13 to 15As shown, the fluid machinery also includes an upper flange 60 and a lower flange 70, which are respectively disposed at both axial ends of the cylinder liner 20. A pressure relief ring groove 61 is formed on the end face of the upper flange 60 facing the cylinder liner 20, which connects the two limiting chambers 311. This ensures that the two limiting chambers 311 are always in a connected state, reducing the compression power consumption of the limiting chambers 311 and improving the compressor's performance and reliability.

[0080] It should be noted that in this application, the pressure relief ring groove 61 is eccentrically positioned.

[0081] Optionally, the eccentricity of the pressure relief ring groove 61 is equal to the eccentricity of the first eccentric part.

[0082] like Figure 12 and Figure 13 As shown, the outer diameter D10 of the pressure relief ring groove 61 and the outer diameter D8 of the cross groove structure 30 satisfy the following condition: 0.1≤D10 / D8≤0.9. This ensures that the cross groove structure 30 and the upper flange 60 have a certain bearing area, reduces frictional power consumption, and improves the performance and reliability of the compressor.

[0083] like Figures 16 to 18 As shown, the cross-section of the pressure relief ring groove 61 is one of the following: circular, square, or elliptical.

[0084] like Figure 9 , Figure 12 , Figure 19 , Figure 20 As shown, the height H2 of the first limiting channel 31 in the axial direction of the cross groove structure 30 and the height H3 of the first eccentric part 11 in the axial direction of the crankshaft 10 satisfy the following: the design range of H2-H3 is 0.5mm to 5mm, so that the height difference between the first limiting channel 31 and the first eccentric part 11 forms a pressure relief channel 80, and the pressure relief channel 80 is used to communicate with the two limiting cavities 311. In this way, the compression power consumption is reduced by utilizing the height difference between the first eccentric part 11 and the first limiting channel 31 of the crankshaft 10. Gas can be depressurized through the pressure relief channel 80 formed by the height difference between the first eccentric part 11 and the first limiting channel 31 of the crankshaft 10. The pressure relief ring groove 61 of the upper flange 60 can be eliminated, the bearing area between the upper flange 60 and the cross groove structure 30 can be increased, and friction and wear can be reduced. While ensuring sufficient pressure relief of the limiting cavity 311, the friction power consumption between the cross groove structure 30 and the cylinder liner 20 is minimized, thereby improving the performance and reliability of the compressor.

[0085] like Figure 21 As shown, in the sliding direction of the first eccentric part 11, a channel pressure relief groove 312 is provided on the channel wall of the first limiting channel 31. The channel pressure relief groove 312 passes through the two radial sides of the cross groove structure 30 and is used to connect the two limiting cavities 311.

[0086] like Figure 22 As shown, two crankshaft pressure relief grooves 111 are provided on the end face of the first eccentric part 11 away from the second eccentric part 12. The two crankshaft pressure relief grooves 111 are located on both sides of the line connecting the proximal and distal ends of the first eccentric part 11. Two connecting notches 112 are provided on the outer peripheral surface of the first eccentric part 11. The two connecting notches 112 are located on both sides of the line connecting the proximal and distal ends of the first eccentric part 11. Each crankshaft pressure relief groove 111 is connected to the corresponding limiting cavity 311 through the connecting notch 112.

[0087] Optionally, the two crankshaft relief grooves 111 have a phase difference of 180°; the two connecting notches 112 have a phase difference of 180°.

[0088] 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.

[0089] Preferably, the first eccentric portion 11 and the second eccentric portion 12 are arranged opposite each other at 180°.

[0090] 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.

[0091] 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.

[0092] 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.

[0093] 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.

[0094] 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.

[0095] 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 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 eccentric distance 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). 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 first eccentric portion (11) is slidably disposed within the first limiting channel (31) and forms a limiting cavity (311). The limiting cavity (311) is located in the sliding direction of the first eccentric portion (11). The slider (40) has a through hole (41), the second eccentric part (12) extends into the through hole (41), the slider (40) is slidably disposed in the second limiting channel (32) and forms a variable volume cavity (321), the variable volume cavity (321) 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 second limiting channel (32) 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); In the sliding direction of the first eccentric part (11), a channel pressure relief groove (312) is provided on the channel wall of the first limiting channel (31). The channel pressure relief groove (312) penetrates the two radial sides of the cross groove structure (30) and is used to connect the two limiting cavities (311). Two crankshaft pressure relief grooves (111) are provided on the end face of the first eccentric part (11) away from the second eccentric part (12). The two crankshaft pressure relief grooves (111) are respectively located on both sides of the line connecting the proximal and distal ends of the first eccentric part (11). Two connecting notches (112) are provided on the outer peripheral surface of the first eccentric part (11). The two connecting notches (112) are located on both sides of the line connecting the proximal and distal ends of the first eccentric part (11). Each crankshaft pressure relief groove (111) is connected to the corresponding limiting cavity (311) through the connecting notch (112).

2. The fluid machinery according to claim 1, characterized in that, The end face of the first eccentric part (11) facing the cross groove structure (30) serves as a thrust surface, so that the first eccentric part (11) makes thrust contact with the cross groove structure (30).

3. The fluid machinery according to claim 1, characterized in that, The height of the first eccentric part (11) in the axial direction of the crankshaft (10) is less than the height of the second eccentric part (12) in the axial direction of the crankshaft (10).

4. The fluid machinery according to claim 1, characterized in that, The height of the first limiting channel (31) in the axial direction of the cross groove structure (30) is less than the height of the second limiting channel (32) in the axial direction of the cross groove structure (30).

5. The fluid machinery according to claim 1, characterized in that, The first limiting channel (31) 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 second limiting channel (32).

6. The fluid machinery according to claim 1, 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 D1 of the first eccentric part (11), the diameter D2 of the second eccentric part (12), and the diameter D3 of the central hole (34) satisfy the following relationship: D1 > D3 > D2.

7. The fluid machinery according to claim 1, 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 D4 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 D2 of the second eccentric portion (12) satisfy the following: D4 + 2 × e + 2 × L1 = D2, D2 + 2 L5 = D3, where e is the eccentricity of the first eccentric part (11), L1 is the first 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 of the center hole (34) when the second eccentric part (12) is concentric with the center hole (34).

8. The fluid machinery according to claim 7, characterized in that, The design range of the first reserved gap L1 is 0.05mm to 3mm.

9. The fluid machinery according to claim 7, characterized in that, The design range of the fifth reserved gap L5 is 0.05mm to 5mm.

10. The fluid machinery according to claim 1, characterized in that, The height H2 of the first limiting channel (31) in the axial direction of the cross groove structure (30) and the height H3 of the first eccentric part (11) in the axial direction of the crankshaft (10) satisfy the following condition: 0.05≤H3 / H2<1.

11. The fluid machinery according to claim 1, characterized in that, There is a second reserved gap L2 between the outer peripheral surface of the first eccentric part (11) and the channel wall of the first limiting channel (31), and the design range of the second reserved gap L2 is 0.008mm~0.05mm.

12. The fluid machinery according to claim 1, characterized in that, The projection of the slider (40) in its sliding direction is circular, the projection of the second limiting channel (32) in the sliding direction of the slider (40) is circular, and there is a third reserved gap L3 between the outer peripheral surface of the slider (40) and the channel wall of the second limiting channel (32), and the design range of the third reserved gap L3 is 0.008mm~0.05mm.

13. The fluid machinery according to claim 1, characterized in that, The fluid machinery also includes: The upper flange (60) and the lower flange (70) are respectively disposed at both ends of the cylinder liner (20). The upper flange (60) has a pressure relief ring groove (61) on the end face facing the cylinder liner (20). The pressure relief ring groove (61) is used to connect the two limiting cavities (311).

14. The fluid machinery according to claim 13, characterized in that, The pressure relief ring groove (61) is eccentrically positioned.

15. The fluid machinery according to claim 13, characterized in that, The outer diameter D10 of the pressure relief ring groove (61) and the outer diameter D8 of the cross groove structure (30) satisfy the following condition: 0.1≤D10 / D8≤0.

9.

16. The fluid machinery according to claim 13, characterized in that, The cross-section of the pressure relief ring groove (61) is one of the following: circular, square, or elliptical.

17. The fluid machinery according to any one of claims 1 to 16, characterized in that, The height H2 of the first limiting channel (31) in the axial direction of the cross groove structure (30) and the height H3 of the first eccentric part (11) in the axial direction of the crankshaft (10) satisfy the following: the design range of H2-H3 is 0.5mm~5mm, so that the height difference between the first limiting channel (31) and the first eccentric part (11) forms a pressure relief channel (80), and the pressure relief channel (80) is used to communicate with the two limiting cavities (311).

18. The fluid machinery according to any one of claims 1 to 16, characterized in that, The two crankshaft pressure relief grooves (111) have a phase difference of 180°; The two connecting gaps (112) have a phase difference of 180°.

19. The fluid machinery according to any one of claims 1 to 16, 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.

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

21. 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 20.

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