Pump body assembly, rotary cylinder pump and heat exchange device

Abstract

The application provides a pump body assembly, a rotating cylinder pump and a heat exchange device, the pump body assembly comprising a rotating shaft, a cylinder sleeve, a piston sleeve and a piston, the rotating shaft being provided with two eccentric parts along the axial direction of the rotating shaft; the rotating shaft is eccentrically arranged with the cylinder sleeve and the eccentric distance is fixed; the piston sleeve is rotatably arranged in the cylinder sleeve, the extension direction of the limiting channel of the piston sleeve is perpendicular to the axial direction of the rotating shaft; the two eccentric parts correspondingly extend into the two through holes of the two pistons, the two pistons are correspondingly arranged in the two limiting channels in a sliding mode and form a variable volume cavity; the two liquid discharge ports are arranged at intervals along the axial direction of the cylinder sleeve, the height H2 of the connecting part between the two liquid discharge ports in the axial direction of the cylinder sleeve and the height H q2 of the connecting part between the two limiting channels in the axial direction of the piston sleeve are in the range of 0.9-3. The application solves the problems of the prior art, i.e. the machining process of the cylinder sleeve is relatively complex, the manufacturing cost of the fluorine pump is relatively high, the economy of the rotating cylinder pump is not good, in addition, the performance and reliability of the existing fluorine pump are poor.

Description

Technical Field

[0001] This invention relates to the field of heat exchange system technology, and more specifically, to a pump body assembly, a rotary pump, and a heat exchange device. Background Technology

[0002] In fields such as data centers and computer room air conditioning, liquid pumps are often used instead of compressors to drive refrigerant in the air conditioning system. This method is more energy efficient than conventional air conditioning systems. In the industry, this type of system that uses a pump to drive the refrigerant is called a fluorine pump system, and the pump that drives the refrigerant is called a fluorine pump.

[0003] However, the machining process of cylinder liners for existing fluorinated pumps is relatively complex, resulting in high manufacturing costs and hindering the economic efficiency of rotary pumps. In addition, the performance and reliability of existing fluorinated pumps are poor. Summary of the Invention

[0004] The main objective of this invention is to provide a pump body assembly, a rotary cylinder pump, and a heat exchange device to solve the problems of the complex cylinder liner processing technology in the prior art, which leads to high manufacturing costs of fluorine pumps and is not conducive to the economy of rotary cylinder pumps. In addition, the existing fluorine pumps have poor performance and reliability.

[0005] To achieve the above objectives, according to one aspect of the present invention, a pump body assembly is provided, comprising a rotating shaft, a cylinder liner, a piston sleeve, and a piston, wherein the rotating shaft has two eccentric portions arranged along its axial direction; the rotating shaft is eccentrically arranged with a fixed eccentric distance from the cylinder liner; the piston sleeve is rotatably disposed within the cylinder liner, and the piston sleeve has two limiting channels, the two limiting channels being sequentially arranged along the axial direction of the rotating shaft, the extending direction of the limiting channels being perpendicular to the axial direction of the rotating shaft; the piston has a through hole, there are two pistons, the two eccentric portions correspondingly extend into the two through holes of the two pistons, and the two pistons are correspondingly slidably disposed within the two limiting channels to form a variable volume cavity. The variable volume chamber is located in the sliding direction of the piston. The rotating shaft drives the piston to reciprocate within the limiting channel while interacting with the piston sleeve, causing both the piston and the sleeve to rotate within the cylinder liner. The cylinder liner is equipped with a suction port and a discharge port. The suction port communicates with the variable volume chamber and supplies refrigerant into it. The discharge port communicates with the variable volume chamber and discharges the refrigerant from within it. There are two discharge ports, spaced apart along the axial direction of the cylinder liner. The height H2 of the connection between the two discharge ports along the axial direction of the cylinder liner is equal to the height H of the connection between the two limiting channels along the axial direction of the piston sleeve. q2 The ratio ranges from 0.9 to 3.

[0006] Furthermore, the height H2 of the connection between the two drain ports in the axial direction of the cylinder liner and the height H of the connection between the two limiting channels in the axial direction of the piston sleeve are... q2 The ratio ranges from 1.1 to 1.2.

[0007] Furthermore, there are two drain ports, which are spaced apart along the axial direction of the cylinder liner. Neither drain port penetrates the axial end face of the cylinder liner. The ratio of the height H2 of the connection between the two drain ports in the axial direction of the cylinder liner to the height H1 of the cylinder liner in the axial direction ranges from 0.1 to 0.3.

[0008] Furthermore, there are two drain ports, which are spaced apart along the axial direction of the cylinder liner. Neither drain port penetrates the axial end face of the cylinder liner. The ratio of the depth H5 of the upper drain port in the axial direction of the cylinder liner to the height H1 of the cylinder liner in the axial direction ranges from 0.05 to 0.4.

[0009] Furthermore, there are two drain ports, which are spaced apart along the axial direction of the cylinder liner. Neither drain port penetrates the axial end face of the cylinder liner. The ratio of the depth H6 of the lower drain port in the axial direction of the cylinder liner to the height H1 of the cylinder liner in the axial direction ranges from 0.05 to 0.4.

[0010] Furthermore, there are two drain ports, which are spaced apart along the axial direction of the cylinder liner. The two drain ports pass through the end faces of both ends of the cylinder liner in the axial direction. The ratio of the height H2 of the connection between the two drain ports in the axial direction of the cylinder liner to the height H1 of the cylinder liner in the axial direction ranges from 0.1 to 0.5.

[0011] Furthermore, there are two drain ports, which are spaced apart along the axial direction of the cylinder liner. The two drain ports respectively penetrate the end faces of both ends of the cylinder liner in the axial direction. The ratio of the depth H3 of the upper drain port in the axial direction of the cylinder liner to the height H1 of the cylinder liner in the axial direction ranges from 0.2 to 0.4.

[0012] Furthermore, there are two drain ports, which are spaced apart along the axial direction of the cylinder liner and penetrate the end faces of both ends of the cylinder liner in the axial direction respectively; the ratio of the depth H4 of the lower drain port in the axial direction of the cylinder liner to the height H1 of the cylinder liner in the axial direction is in the range of 0.2 to 0.4.

[0013] Furthermore, there is a phase difference of a first included angle A between the two eccentric parts, the eccentricity of the two eccentric parts is equal, and there is a phase difference of a second included angle B between the extension directions of the two limiting channels, wherein the first included angle A is twice the second included angle B.

[0014] Furthermore, the two eccentric parts are positioned 180° opposite each other.

[0015] According to another aspect of the present invention, a rotary cylinder pump is provided, including a pump body assembly, wherein the pump body assembly is the pump body assembly described above.

[0016] According to another aspect of the present invention, a heat exchange device is provided, including a rotary pump, wherein the rotary pump is the rotary pump described above.

[0017] By applying the technical solution of this invention, the structure of the cylinder liner is optimized. Simultaneously, there are two drain ports, spaced apart along the axial direction of the cylinder liner. The height H2 of the connection between the two drain ports in the axial direction of the cylinder liner is equal to the height H of the connection between the two limiting channels in the axial direction of the piston sleeve. q2 The ratio ranges from 0.9 to 3. This ensures that the cylinder liner manufacturing process is relatively simple, while also ensuring the structural stability of the cylinder liner, preventing deformation during long-term use, and ensuring smooth fluid flow at the suction and discharge ports, thereby ensuring the operational reliability of the rotary pump. Attached Figure Description

[0018] 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:

[0019] Figure 1 A schematic diagram of the pump body assembly according to Embodiment 1 of the present invention is shown;

[0020] Figure 2 It shows Figure 1 A schematic diagram of the cylinder liner structure of the pump body assembly;

[0021] Figure 3 It shows Figure 2 A top-view structural diagram of the cylinder liner;

[0022] Figure 4 It shows Figure 3 A schematic diagram of the structure from the E-direction perspective;

[0023] Figure 5 A schematic diagram of the pump body assembly according to Embodiment 2 of the present invention is shown;

[0024] Figure 6 It shows Figure 5 A schematic diagram of the cylinder liner structure of the pump body assembly;

[0025] Figure 7 It shows Figure 6 A top-view structural diagram of the cylinder liner;

[0026] Figure 8 It shows Figure 7 A schematic diagram of the structure from the F-direction perspective;

[0027] Figure 9A schematic diagram of the piston sleeve of a pump body assembly according to an optional embodiment of the present invention is shown;

[0028] Figure 10 It shows Figure 9 A cross-sectional view of the piston sleeve from the ZZ perspective.

[0029] Figure 11 It shows Figure 9 A top-view structural diagram of the piston sleeve.

[0030] The above figures include the following reference numerals:

[0031] 10. Shaft;

[0032] 20. Cylinder liner; 21. Suction port; 22. Drain port; 23. Buffer tank; 24. Suction tank;

[0033] 31. Piston sleeve; 311. Limiting channel;

[0034] 40. Flange; 41. Upper flange; 42. Lower flange. Detailed Implementation

[0035] 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.

[0036] To address the problems of complex cylinder liner manufacturing processes in existing technologies, which lead to high manufacturing costs for fluorine pumps and hinder the economic efficiency of rotary cylinder pumps, as well as the poor performance and reliability of existing fluorine pumps, this invention provides a pump body assembly, a rotary cylinder pump, and a heat exchange device. The rotary cylinder pump includes a pump body assembly, which is the pump body assembly described above and below. The heat exchange device includes a rotary cylinder pump, which is the rotary cylinder pump described above.

[0037] like Figures 1 to 4As shown, the pump assembly includes a rotating shaft 10, a cylinder liner 20, a piston sleeve 31, and a piston. The rotating shaft 10 has two eccentric portions along its axial direction. The rotating shaft 10 is eccentrically positioned to the cylinder liner 20 with a fixed eccentricity. The piston sleeve 31 is rotatably disposed within the cylinder liner 20 and has two limiting channels 311. The two limiting channels 311 are sequentially arranged along the axial direction of the rotating shaft 10, and their extension direction is perpendicular to the axial direction of the rotating shaft 10. Two pistons have through holes. The two eccentric portions extend into the two through holes of the two pistons respectively. The two pistons are slidably disposed within the two limiting channels 311, forming a variable volume cavity. The variable volume cavity is located in the sliding direction of the piston. Upward, the rotating shaft 10 rotates to drive the piston to slide back and forth within the limiting channel 311 while interacting with the piston sleeve 31, so that the piston sleeve 31 and the piston rotate within the cylinder sleeve 20; the cylinder sleeve 20 is provided with a suction port 21 and a discharge port 22. The suction port 21 communicates with the variable volume cavity and supplies refrigerant into the variable volume cavity, while the discharge port 22 communicates with the variable volume cavity and discharges the refrigerant from the variable volume cavity through the discharge port 22; there are two discharge ports 22, which are spaced apart along the axial direction of the cylinder sleeve 20. The height H2 of the connection between the two discharge ports 22 in the axial direction of the cylinder sleeve 20 is equal to the height H of the connection between the two limiting channels 311 in the axial direction of the piston sleeve 31. q2 The ratio ranges from 0.9 to 3.

[0038] By optimizing the structure of the cylinder liner 20, and providing two drain ports 22 spaced apart along the axial direction of the cylinder liner 20, the height H2 of the connection between the two drain ports 22 in the axial direction of the cylinder liner 20 is equal to the height H of the connection between the two limiting channels 311 in the axial direction of the piston sleeve 31. q2 The ratio ranges from 0.9 to 3. This ensures that the machining process of cylinder liner 20 is relatively simple, while also ensuring the structural stability of cylinder liner 20, ensuring that cylinder liner 20 does not deform as much as possible during long-term use, and ensuring smooth fluid flow at suction port 21 and discharge port 22, thereby ensuring the operational reliability of rotary pump.

[0039] It should be noted that in this embodiment, considering the structural stability of the pump body assembly, its resistance to deformation, and to ensure a sufficiently large inlet and outlet flow area for smooth flow, such as... Figure 4 and Figure 10 As shown, the height H2 of the connection between the two drain ports 22 in the axial direction of the cylinder liner 20 and the height H of the connection between the two limiting channels 311 in the axial direction of the piston sleeve 31 are... q2 The ratio ranges from 1.1 to 1.2.

[0040] like Figure 2 and Figure 3As shown, the cylinder liner 20 also includes a buffer groove 23 and a liquid suction groove 24. The inner wall surface of the cylinder liner 20 has a liquid suction groove 24, which is connected to the liquid suction port 21 through the buffer groove 23.

[0041] like Figure 4 As shown, there are two drain ports 22, which are spaced apart along the axial direction of the cylinder liner 20. Neither drain port 22 penetrates the axial end face of the cylinder liner 20. The ratio of the height H2 of the connection between the two drain ports 22 in the axial direction of the cylinder liner 20 to the height H1 of the cylinder liner 20 in the axial direction ranges from 0.1 to 0.3.

[0042] like Figure 4 As shown, there are two drain ports 22, which are spaced apart along the axial direction of the cylinder liner 20. Neither drain port 22 penetrates the axial end face of the cylinder liner 20. The ratio of the depth H5 of the upper drain port 22 in the axial direction of the cylinder liner 20 to the height H1 of the cylinder liner 20 in the axial direction ranges from 0.05 to 0.4.

[0043] like Figure 4 As shown, there are two drain ports 22, which are spaced apart along the axial direction of the cylinder liner 20. Neither drain port 22 penetrates the axial end face of the cylinder liner 20. The ratio of the depth H6 of the lower drain port 22 in the axial direction of the cylinder liner 20 to the height H1 of the cylinder liner 20 in the axial direction ranges from 0.05 to 0.4.

[0044] Example 2

[0045] It should be noted that, in this embodiment, the difference from Embodiment 1 is that, as shown in the following... Figures 5 to 8 As shown, the drain port of the cylinder liner 20 in this embodiment is an open type.

[0046] like Figure 8 As shown, there are two drain ports 22, which are spaced apart along the axial direction of the cylinder liner 20. The two drain ports 22 respectively penetrate the end faces of both ends of the cylinder liner 20 in the axial direction. The ratio of the height H2 of the connection between the two drain ports 22 in the axial direction of the cylinder liner 20 to the height H1 of the cylinder liner 20 in the axial direction is in the range of 0.1 to 0.5.

[0047] like Figure 8 As shown, there are two drain ports 22, which are spaced apart along the axial direction of the cylinder liner 20. The two drain ports 22 respectively penetrate the end faces of both ends of the cylinder liner 20 in the axial direction. The ratio of the depth H3 of the upper drain port 22 in the axial direction of the cylinder liner 20 to the height H1 of the cylinder liner 20 in the axial direction ranges from 0.2 to 0.4.

[0048] like Figure 8As shown, there are two drain ports 22, which are spaced apart along the axial direction of the cylinder liner 20. The two drain ports 22 respectively penetrate the end faces of both ends of the cylinder liner 20 in the axial direction. The ratio of the depth H4 of the lower drain port 22 in the axial direction of the cylinder liner 20 to the height H1 of the cylinder liner 20 in the axial direction ranges from 0.2 to 0.4.

[0049] It should be noted that, in this application, if Figures 9 to 11 As shown, there is a phase difference of a first included angle A between the two eccentric parts, the eccentricity of the two eccentric parts is equal, and there is a phase difference of a second included angle B between the extension directions of the two limiting channels 311, wherein the first included angle A is twice the second included angle B.

[0050] Preferably, the two eccentric parts are arranged opposite each other at 180°.

[0051] It should be noted that in this application, the cylinder liner 20 has a closed outlet, such as... Figures 1 to 4 As shown, the outlet consists of two rectangular channels running horizontally from the side of the outlet, which connect the outer side of the outlet with the inner circular space inside the cylinder liner 20. The closed end face design makes the structure of the cylinder liner 20 more stable, but it is more difficult to process. After machining, the parts need to be deburred and flanged. The closed structure is prone to generating burrs and flanging during processing, and it is not easy to remove burrs and flanging from the closed structure.

[0052] It should be noted that in this application, the cylinder liner 20 is in an open form, as shown below. Figures 5 to 8 As shown, its appearance resembles a groove dug downwards from the end face of the cylinder liner 20. The flange 40 includes an upper flange 41 and a lower flange 42, which are respectively located at the axial ends of the cylinder liner 20. When the end faces of the upper flange 41 and the lower flange 42 are respectively attached to the upper and lower end faces of the cylinder liner 20, the two grooves of the cylinder liner 20 are enclosed to form two channels. These channels connect the inner circular space inside the cylinder liner 20 and the space outside the cylinder liner 20. The open end face structure is not prone to burrs and flanges, and the burrs and flanges of the open structure are also easier to clean. However, the connection in the middle of the open end face structure is relatively weak, not very stable, and prone to deformation.

[0053] 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.

[0054] 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.

[0055] 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.

[0056] 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.

[0057] 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.

[0058] 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 pump body assembly for use in a fluorine pump, characterized in that, include: A rotating shaft (10) is provided with two eccentric portions along its axial direction; Cylinder liner (20), the rotating shaft (10) is eccentrically set with the cylinder liner (20) and the eccentric distance is fixed; Piston sleeve (31), the piston sleeve (31) is rotatably disposed in the cylinder sleeve (20), the piston sleeve (31) has two limiting channels (311), the two limiting channels (311) are arranged sequentially along the axial direction of the rotating shaft (10), and the extending direction of the limiting channels (311) is perpendicular to the axial direction of the rotating shaft (10); The piston has a through hole, and there are two pistons. The two eccentric parts extend into the two through holes of the two pistons respectively. The two pistons are slidably disposed in the two limiting channels (311) and form a variable volume cavity. The variable volume cavity is located in the sliding direction of the piston. The rotating shaft (10) rotates to drive the piston to slide back and forth in the limiting channel (311) while interacting with the piston sleeve (31) so that the piston sleeve (31) and the piston rotate in the cylinder liner (20). The cylinder liner (20) is provided with a liquid suction port (21) and a liquid discharge port (22). The liquid suction port (21) is connected to the variable volume cavity and supplies refrigerant into the variable volume cavity. The liquid discharge port (22) is connected to the variable volume cavity and discharges the refrigerant in the variable volume cavity from the liquid discharge port (22). There are two drain ports (22), and the two drain ports (22) are spaced apart along the axial direction of the cylinder liner (20); The connection point between the two drain ports (22) is at a height H2 in the axial direction of the cylinder liner (20), and the connection point between the two limiting channels (311) is at a height H in the axial direction of the piston sleeve (31). q2 The ratio ranges from 1.1 to 1.2; The two drain ports (22) respectively penetrate the end faces of the two ends of the cylinder liner (20) in the axial direction; The ratio of the height H2 of the connection between the two drain ports (22) in the axial direction of the cylinder liner (20) to the height H1 of the cylinder liner (20) in the axial direction is in the range of 0.1 to 0.

5. The ratio of the depth H3 of the upper drain port (22) in the axial direction of the cylinder liner (20) to the height H1 of the cylinder liner (20) in the axial direction ranges from 0.2 to 0.

4.

2. The pump body assembly according to claim 1, characterized in that, The ratio of the depth H4 of the lower drain port (22) in the axial direction of the cylinder liner (20) to the height H1 of the cylinder liner (20) in the axial direction ranges from 0.2 to 0.

4.

3. The pump body assembly according to any one of claims 1 to 2, characterized in that, There is a phase difference of a first included angle A between the two eccentric portions, the eccentricity of the two eccentric portions is equal, and there is a phase difference of a second included angle B between the extension directions of the two limiting channels (311), wherein the first included angle A is twice the second included angle B.

4. The pump body assembly according to claim 3, characterized in that, The two eccentric portions are arranged opposite each other at 180°.

5. A rotary cylinder pump, characterized in that, It includes a pump body assembly, which is the pump body assembly according to any one of claims 1 to 4.

6. A heat exchange device, characterized in that, Includes a rotary cylinder pump, wherein the rotary cylinder pump is the rotary cylinder pump as described in claim 5.

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