Fluid machine and heat exchange device

Abstract

The application provides a fluid machine and a heat exchange device, and the fluid machine comprises a crankshaft, a cylinder sleeve, a cross groove structure, a first sliding block and a second sliding block, 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, and a first limiting channel and a second limiting channel of the cross groove structure are sequentially arranged along the axial direction of the crankshaft; the first eccentric part extends into a first through hole of the first sliding block, the first sliding block is slidingly arranged in the first limiting channel and forms a first variable volume cavity; the second eccentric part extends into a second through hole of the second sliding block, the second sliding block is slidingly arranged in the second limiting channel and forms a second variable volume cavity; and the height of the first sliding block in the axial direction of the cylinder sleeve is less than the height of the second sliding block in the axial direction of the cylinder sleeve. The application solves the problems of low energy efficiency and large noise 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] Based on consumer demands for air conditioning comfort, the air conditioning industry has consistently pursued high efficiency and low noise. The compressor, as the heart of the air conditioner, directly impacts its energy efficiency and noise levels. Scroll compressors, as the mainstream type of household air conditioner compressor, have matured after nearly a century of development, but their structural principles limit further 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 in existing compressors.

[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 first slider, and a second 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 first slider has a first through hole, the first eccentric portion extending into the first through hole, and the first slider being slidably disposed within the first limiting channel and forming a first variable volume. The first variable volume cavity is located in the sliding direction of the first slider. The crankshaft rotates to drive the first slider to slide back and forth in the first limiting channel while interacting with the cross groove structure, so that the cross groove structure and the first slider rotate within the cylinder liner. The second slider has a second through hole, and a second eccentric part extends into the second through hole. The second slider is slidably disposed in the second limiting channel and forms a second variable volume cavity. The second variable volume cavity is located in the sliding direction of the second slider. The crankshaft rotates to drive the second slider to slide back and forth in the second limiting channel while interacting with the cross groove structure, so that the cross groove structure and the second slider rotate within the cylinder liner. The first limiting channel extends directly through the cross groove structure along the axial direction to the end face of the cross groove structure, so that one end of the cross groove structure is open.

[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 slider in the axial direction of the cylinder liner is less than the height of the second slider in the axial direction of the cylinder liner.

[0009] Furthermore, the height of the first slider in the axial direction of the cylinder liner is less than the height of the second slider in the axial direction of the cylinder liner.

[0010] Furthermore, the end face of the cross groove structure without an open end has a pre-reserved 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.

[0011] 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.

[0012] 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.

[0013] Furthermore, the design range of the first reserved gap L1 is 0.05mm to 3mm.

[0014] Furthermore, the design range of the fifth reserved gap L5 is 0.05mm to 5mm.

[0015] Furthermore, the projection of the first slider in its sliding direction is square, and the projection of the second slider in its sliding direction is circular.

[0016] Furthermore, the width B1 of the first slider and the outer diameter D5 of the second slider satisfy the following condition: 0.5≤B1 / D5≤1.5.

[0017] Furthermore, the height H1 of the first slider in the axial direction of the cylinder liner and the outer diameter D5 of the second slider satisfy the following condition: 0.5 ≤ H1 / D5 < 1.

[0018] Furthermore, in a direction perpendicular to the sliding direction of the first slider, there is a second reserved gap L2 between the outer surface of the first slider 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.

[0019] Furthermore, there is a third reserved gap L3 between the outer peripheral surface of the second slider and the channel wall of the second limiting channel, and the design range of the third reserved gap L3 is 0.008mm to 0.05mm.

[0020] 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.

[0021] Furthermore, the first eccentric part and the second eccentric part are arranged opposite each other at 180°.

[0022] 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.

[0023] The present invention provides a semi-enclosed double-cylinder four-compression structure. By configuring the cross-groove structure with a first limiting channel and a second limiting channel, a first slider is slidably disposed within the first limiting channel to form a first variable volume cavity. The first variable volume cavity is located in the sliding direction of the first slider. The crankshaft rotates to drive the first slider to reciprocate within the first limiting channel while interacting with the cross-groove structure, causing the cross-groove structure and the first slider to rotate within the cylinder liner. Furthermore, a second slider is slidably disposed within the second limiting channel to form a second variable volume cavity. The second variable volume cavity is located in the sliding direction of the second slider. The crankshaft rotates to drive the second slider to reciprocate within the second limiting channel while interacting with the cross-groove structure, causing the cross-groove structure and the second slider to rotate within the cylinder liner. 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.

[0024] Furthermore, since the fluid machinery provided in this application can operate stably, that is, it ensures that the compressor has high energy efficiency, low noise and vibration, simple assembly, and good manufacturability of parts, thereby ensuring the working reliability of the heat exchange equipment. Attached Figure Description

[0025] 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:

[0026] Figure 1 A schematic diagram of the pump body assembly of a compressor according to an optional embodiment of the present invention is shown;

[0027] Figure 2 It shows Figure 1 An exploded view of the pump body components;

[0028] Figure 3 It shows Figure 1 A schematic diagram of the crankshaft, cross groove structure, and first slider of the pump body assembly in the assembly state;

[0029] Figure 4 It shows Figure 3 A structural schematic diagram of the crankshaft, cross groove structure, and first slider from another perspective;

[0030] Figure 5 It shows Figure 1 A schematic diagram of the pump body assembly in the diagram;

[0031] Figure 6 It shows Figure 5 A magnified structural diagram of the CC section;

[0032] Figure 7 It shows Figure 5 A magnified structural diagram of the DD section;

[0033] Figure 8 It shows Figure 2 A schematic diagram of the crankshaft structure of the pump body assembly;

[0034] Figure 9 It shows Figure 2 A schematic diagram of the cross-groove structure of the pump body assembly;

[0035] Figure 10 It shows Figure 4 The cross groove structure and the structural diagram of the crankshaft in the assembly state from a top view.

[0036] Figure 11 It shows Figure 2 A schematic diagram of the structure of the second slider of the pump body assembly;

[0037] Figure 12 It shows Figure 2 A schematic diagram of the cross-groove structure of the pump body assembly.

[0038] Figure 13 It shows Figure 2 A schematic diagram of the structure of the first slider of the pump body assembly;

[0039] Figure 14 It shows Figure 2 A schematic diagram of the cross-groove structure of the pump body assembly from another perspective;

[0040] Figure 15 The noise comparison curves of a single-cylinder dual-compression compressor and a semi-enclosed cross-groove compressor are shown in the noise range of 0-1.2kHz.

[0041] Figure 16 The noise comparison curves of a single-cylinder dual-compression compressor and a semi-enclosed cross-groove compressor are shown in the noise range of 0-12.8kHz.

[0042] Figure 17 A comparison curve of the cooling capacity of a compressor with a single-cylinder dual-compression structure and a compressor with a semi-enclosed cross-slot structure under the same conditions is shown.

[0043] Figure 18 The power consumption comparison curves of a compressor with a single-cylinder dual-compression structure and a compressor with a semi-enclosed cross-groove structure are shown under the same conditions.

[0044] Figure 19 The performance comparison curves of a compressor with a single-cylinder dual-compression structure and a compressor with a semi-enclosed cross-groove structure are shown under the same conditions.

[0045] Figure 20 It shows Figure 1 A top-view structural diagram of the crankshaft shaft body and the second eccentric part.

[0046] The above figures include the following reference numerals:

[0047] 10. Crankshaft; 11. First eccentric part; 12. Second eccentric part;

[0048] 20. Cylinder liner;

[0049] 30. Cross-groove structure; 31. First limiting channel; 311. First variable volume cavity; 32. Second limiting channel; 321. Second variable volume cavity; 33. Opening; 34. Center hole;

[0050] 40. First slider; 41. First through hole;

[0051] 50. Second slider; 51. Second through hole;

[0052] 60. Upper flange; 70. 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] 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.

[0055] like Figures 1 to 20 As shown, the fluid machinery includes a crankshaft 10, a cylinder liner 20, a cross-groove structure 30, a first slider 40, and a second slider 50. The crankshaft 10 has a first eccentric portion 11 and a second eccentric portion 12 along its axial direction. The crankshaft 10 is eccentrically positioned with a fixed eccentricity to the cylinder liner 20. The cross-groove structure 30 is rotatably disposed within the cylinder liner 20 and 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, with the first limiting channel 31 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 first slider 40 has a first through hole 41, with the first eccentric portion 11 extending into the first through hole 41. The first slider 40 is slidably disposed within the first limiting channel 31, forming a first variable volume cavity 311. Located in the sliding direction of the first slider 40, the crankshaft 10 rotates to drive the first 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 first slider 40 rotate within the cylinder liner 20; the second slider 50 has a second through hole 51, the second eccentric part 12 extends into the second through hole 51, the second slider 50 is slidably disposed in the second limiting channel 32 and forms a second variable volume cavity 321, the second variable volume cavity 321 is located in the sliding direction of the second slider 50, the crankshaft 10 rotates to drive the second slider 50 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 second slider 50 rotate within the cylinder liner 20; wherein, the first limiting channel 31 directly penetrates along the axial direction of the cross groove structure 30 to the end face of the cross groove structure 30, so that one end of the cross groove structure 30 is open.

[0056] This application provides a dual-cylinder four-compression structure. By configuring the cross-groove structure 30 with a first limiting channel 31 and a second limiting channel 32, the first slider 40 is slidably disposed within the first limiting channel 31 to form a first variable volume cavity 311. The first variable volume cavity 311 is located in the sliding direction of the first slider 40. The crankshaft 10 rotates to drive the first 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 first slider 40 rotate within the cylinder liner 20. In addition, the second slider 50 is slidably disposed within the second limiting channel 32 to form a second variable volume cavity 321. The second variable volume cavity 321 is located in the sliding direction of the second slider 50. The crankshaft 10 rotates to drive the second slider 50 to reciprocate within the second limiting channel 32 while interacting with the cross-groove structure 30, so that the cross-groove structure 30 and the second slider 50 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, thereby ensuring the working reliability of the heat exchange equipment.

[0057] Furthermore, since the fluid machinery provided in this application can operate stably, that is, it ensures that the compressor has high energy efficiency, low noise and vibration, simple assembly, and good manufacturability of parts, thereby ensuring the working reliability of the heat exchange equipment.

[0058] It should be noted that this application proposes a novel dual-cylinder, four-compression, semi-enclosed cross-groove compressor. Based on the cross-groove structure with two limiting channels and the mechanism principle of a 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-groove structure 30 with the first limiting channel 31 and the second limiting channel 32, the first slider 40, and the second slider 50.

[0059] 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.

[0060] 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 ensures that the thrust surface in this application does not bear load with the upper flange 60, thereby reducing wear on the end face of the upper flange 60 and improving the reliability of the compressor.

[0061] 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 8 As shown, the height of the first eccentric portion 11 in the axial direction of the crankshaft 10 is less than the height of the second eccentric portion 12 in the axial direction of the crankshaft 10. The height of the first slider 40 in the axial direction of the cylinder liner 20 is less than the height of the second slider 50 in the axial direction of the cylinder liner 20. This ensures the assembly reliability when the first eccentric portion 11 extends into the first through hole 41 of the first slider 40, and also ensures the assembly reliability when the second eccentric portion 12 extends into the second through hole 51 of the second slider 50.

[0062] like Figures 2 to 4 , Figure 12 , Figure 14 As shown, the end face of the non-open end of the cross groove structure 30 has a pre-drilled hole 33 for the crankshaft 10 to extend out. The hole 33 is concentrically arranged with the cross groove structure 30 and communicates with the second limiting channel 32. In this way, the hole 33 ensures that the shaft part of the crankshaft 10 can pass through, thus ensuring the feasibility of assembly between the two.

[0063] 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 8 and Figure 9 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.

[0064] like Figure 10As 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 and the central hole 34 are concentric. This ensures the assembly feasibility of the pump body assembly.

[0065] 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.

[0066] Optionally, the design range of the fifth reserved gap L5 is 0.05mm to 5mm.

[0067] like Figure 11 and Figure 13 As shown, the projection of the first slider 40 in its sliding direction is square, and the projection of the second slider 50 in its sliding direction is circular.

[0068] like Figure 11 and Figure 13 As shown, the width B1 of the first slider 40 and the outer diameter D5 of the second slider 50 satisfy the following condition: 0.5 ≤ B1 / D5 ≤ 1.5. This ensures that the compressor's energy efficiency does not decrease, while reducing compressor noise and vibration, and improving compressor reliability.

[0069] like Figure 11 and Figure 13 As shown, the height H1 of the first slider 40 in the axial direction of the cylinder liner 20 and the outer diameter D5 of the second slider 50 satisfy the following condition: 0.5 ≤ H1 / D5 < 1. This ensures that the compressor's energy efficiency does not decrease, while reducing compressor noise and vibration, and improving compressor reliability.

[0070] It should be noted that in this application, in a direction perpendicular to the sliding direction of the first slider 40, there is a second reserved gap L2 between the outer surface of the first slider 40 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. This helps to reduce compressor leakage and power consumption, and also helps to improve the energy efficiency of the compressor.

[0071] It should be noted that in this application, there is a third reserved gap L3 between the outer peripheral surface of the second slider 50 and the channel wall of the second limiting channel 32, and the design range of the third reserved gap L3 is 0.008mm to 0.05mm. This helps to reduce leakage between the second slider 50 and the cross groove structure 30, thereby improving the cooling capacity and performance of the compressor.

[0072] 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.

[0073] Preferably, the first eccentric portion 11 and the second eccentric portion 12 are arranged opposite each other at 180°.

[0074] It should be noted that in this application, the large mass difference between the first eccentric part 11 and the second eccentric part 12, the limiting block, and the piston of the single-cylinder dual-compression compressor crankshaft 10 leads to an unbalanced centrifugal force between the upper and lower chambers during pump operation, affecting compressor noise and vibration. In contrast, the semi-enclosed cross-groove compressor crankshaft has a smaller mass difference between the upper and lower eccentric parts and the upper and lower sliders, significantly reducing the unbalanced centrifugal force between the upper and lower chambers. Actual tests show a significant advantage in noise and vibration reduction (see...). Figures 15 to 19 ).

[0075] like Figure 15 As shown in the figure, the pump assembly in this application is referred to as the semi-enclosed cross groove. The noise curves of the pump assembly with the single-cylinder dual-compression structure in the prior art are compared under the same conditions. The horizontal axis of the figure is the operating frequency of the compressor, and the vertical axis is the total noise value of the compressor. The dashed line represents the curve of the pump assembly with the single-cylinder dual-compression structure, and the solid line represents the curve of the pump assembly with the semi-enclosed cross groove. In this figure, the total noise value ranges from 0 to 1.2 kHz. It can be clearly seen from the figure that the noise of the semi-enclosed cross groove is lower than that of the pump assembly with the single-cylinder dual-compression structure under the same conditions.

[0076] like Figure 16As shown in the figure, the pump assembly in this application is referred to as the semi-enclosed cross groove. The noise curves of the pump assembly with the single-cylinder dual-compression structure in the prior art are compared under the same conditions. The horizontal axis of the figure is the operating frequency of the compressor, and the vertical axis is the total noise value of the compressor. The dashed line represents the curve of the pump assembly with the single-cylinder dual-compression structure, and the solid line represents the curve of the pump assembly with the semi-enclosed cross groove. In this figure, the total noise value ranges from 0 to 12.8 kHz. It can be clearly seen from the figure that the noise of the semi-enclosed cross groove is lower than that of the pump assembly with the single-cylinder dual-compression structure under the same conditions.

[0077] like Figures 17 to 19 As shown in the figure, the pump body assembly in this application is referred to as the semi-enclosed cross groove. A comparison of the cooling capacity, power consumption, and performance curves of the pump body assembly with the existing single-cylinder dual-compression structure under the same conditions is presented. Figures 17 to 19 The horizontal axis in the graph represents the operating frequency of the compressor. Figure 17 The vertical axis in the graph represents the cooling capacity of the compressor. Figure 18 The vertical axis in the graph represents the compressor's power consumption. Figure 19 The vertical axis represents the compressor's performance. The horizontal line represents the curve of a pump assembly with a single-cylinder, dual-compression structure, while the slanted line represents the curve of a pump assembly with a semi-enclosed cross-groove design. Figures 17 to 19 As can be clearly seen from the diagram, the cooling capacity and performance of the semi-enclosed cross groove are higher than those of the pump body assembly with a single-cylinder dual-compression structure under the same conditions, while the power consumption of the semi-enclosed cross groove is lower than that of the pump body assembly with a single-cylinder dual-compression structure under the same conditions.

[0078] It should be noted that in this application, the compressor parts of the twin-cylinder four-compression compressor have high precision requirements, complex processes, and many leakage surfaces, resulting in large leakage and unstable performance of the compressor. The lower slide and cross groove parts of the semi-hermetic cross groove compressor are simple to process and have good manufacturability. At the same time, the compressor has good sealing performance and less leakage. Actual tests show that the compressor cooling capacity is increased, power consumption is reduced, and energy efficiency is improved.

[0079] It should be noted that the technical problem solved and the beneficial effects in this application are as follows:

[0080] 1. It avoids the dead point problem inherent in compressors, reduces leakage losses, and improves compressor efficiency;

[0081] 2. Reduced wear on the end face of the upper flange, improving compressor reliability;

[0082] 3. The pump body components have been simplified, which helps to save costs, optimizes the assembly process, and the parts have good manufacturability, making it easy to ensure assembly and machining accuracy;

[0083] 4. While taking into account energy efficiency, it also has certain advantages in terms of noise and vibration.

[0084] 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.

[0085] 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.

[0086] 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.

[0087] 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.

[0088] 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.

[0089] 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 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 first slider (40) has a first through hole (41), the first eccentric part (11) extends into the first through hole (41), the first slider (40) is slidably disposed in the first limiting channel (31) and forms a first variable volume cavity (311), the first variable volume cavity (311) is located in the sliding direction of the first slider (40), the crankshaft (10) rotates to drive the first 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 first slider (40) rotate in the cylinder liner (20); The second slider (50) has a second through hole (51), the second eccentric part (12) extends into the second through hole (51), the second slider (50) is slidably disposed in the second limiting channel (32) and forms a second variable volume cavity (321), the second variable volume cavity (321) is located in the sliding direction of the second slider (50), the crankshaft (10) rotates to drive the second slider (50) 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 second slider (50) rotate in the cylinder liner (20); 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 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).

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 slider (40) in the axial direction of the cylinder liner (20) is less than the height of the second slider (50) in the axial direction of the cylinder liner (20).

5. The fluid machinery according to claim 1, characterized in that, The cross groove structure (30) has an opening (33) on the end face of the non-open end for the crankshaft (10) to extend out. The opening (33) is concentrically arranged with the cross groove structure (30) and 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 design range of the first reserved gap L1 is 0.05mm to 3mm.

8. The fluid machinery according to claim 1, characterized in that, The design range of the fifth reserved gap L5 is 0.05mm to 5mm.

9. The fluid machinery according to claim 1, characterized in that, The projection of the first slider (40) in its sliding direction is square, and the projection of the second slider (50) in its sliding direction is circular.

10. The fluid machinery according to claim 9, characterized in that, The width B1 of the first slider (40) and the outer diameter D5 of the second slider (50) satisfy the following condition: 0.5≤B1 / D5≤1.

5.

11. The fluid machinery according to claim 9, characterized in that, The height H1 of the first slider (40) in the axial direction of the cylinder liner (20) and the outer diameter D5 of the second slider (50) satisfy the following condition: 0.5 ≤ H1 / D5 < 1.

12. The fluid machinery according to claim 9, characterized in that, In a direction perpendicular to the sliding direction of the first slider (40), there is a second reserved gap L2 between the outer surface of the first slider (40) 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.

13. The fluid machinery according to claim 9, characterized in that, There is a third reserved gap L3 between the outer peripheral surface of the second slider (50) 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.

14. The fluid machinery according to any one of claims 1 to 13, 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.

15. The fluid machinery according to claim 14, characterized in that, The first eccentric part (11) and the second eccentric part (12) are arranged opposite each other at 180°.

16. 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 15.

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