Rotary cylinder pump and heat exchange equipment

Abstract

The utility model provides a rotary cylinder pump and heat exchange equipment, the rotary cylinder pump comprises a rotating shaft, a cylinder sleeve and a piston assembly, the rotating shaft and the cylinder sleeve are eccentrically arranged, and the eccentric distance is fixed; the piston assembly is provided with a variable-volume cavity and is rotatably arranged in the cylinder sleeve, and the rotating shaft is in driving connection with the piston assembly so as to change the volume of the variable-volume cavity; a liquid inlet channel and a liquid discharge channel are arranged on the cylinder sleeve, the liquid inlet channel is communicated with the variable volume cavity and conveys a refrigerant into the variable volume cavity, and the liquid discharge channel is communicated with the variable volume cavity and discharges the refrigerant in the variable volume cavity through the liquid discharge channel; a liquid discharge tail groove is formed in at least one of the liquid discharge starting position and the liquid discharge ending position of the liquid discharge channel so that the communication area of the inner circle of the cylinder sleeve and external high-pressure refrigerants can be increased. The fluorine pump solves the problems that in the prior art, due to the fact that the radial liquid drainage area of an air cylinder is reduced, liquid drainage resistance of the fluorine pump is large in the initial liquid drainage stage and the end liquid drainage stage, and the performance of the fluorine pump is seriously affected.

Description

Technical Field

[0001] The utility model relates to the technical field of heat exchange systems, and in particular, to a rotary cylinder pump and a heat exchange device. Background Art

[0002] With the development of society, the power consumption of data centers has been increasing year by year, resulting in huge power consumption. The computer room air conditioner is an important part of the data center, accounting for 40% of the power consumption of the data center. The application of its energy-saving technology is of great significance.

[0003] A computer room air conditioner is a device used to cool the electrical components in a data center and needs to provide cooling continuously throughout the year to ensure that the indoor temperature can be maintained within a certain range. Most of the existing computer room air conditioners adopt compression refrigeration technology. Whether in summer or winter, they rely on the compression refrigeration system for cooling. When the ambient temperature is high, the existing compression refrigeration technology can meet the performance and energy efficiency requirements; while when the outdoor ambient temperature is significantly lower than the indoor temperature, the most economical and energy-saving cooling method is to use the outdoor low temperature to cool the indoor. The industry has been exploring a low-temperature refrigeration mode that can make full use of outdoor low temperature and has high economy. In recent years, a fluorine pump-compression dual-cycle system has been proposed, that is, in the high-temperature season, the existing compression refrigeration mode is adopted; in the low-temperature season, a low-power fluorine pump is used to replace a high-power compressor as the power source to complete the refrigeration cycle, so as to achieve the energy-saving effect.

[0004] However, in the prior art, since the fluorine pump reduces the radial liquid discharge area of the cylinder, there is a phenomenon that the liquid discharge resistance is relatively large both in the initial stage and the end stage of liquid discharge of the fluorine pump, which seriously affects the performance of the fluorine pump. Summary of the Utility Model

[0005] The main purpose of the present utility model is to provide a rotary cylinder pump and a heat exchange device to solve the problem that in the prior art, due to the reduction of the radial liquid discharge area of the cylinder by the fluorine pump, there is a phenomenon that the liquid discharge resistance is relatively large both in the initial stage and the end stage of liquid discharge of the fluorine pump, which seriously affects the performance of the fluorine pump.

[0006] To achieve the above purpose, according to one aspect of the present utility model, a rotary cylinder pump is provided, including a rotating shaft, a cylinder sleeve and a piston assembly. Among them, the rotating shaft and the cylinder sleeve are eccentrically arranged with a fixed eccentric distance; the piston assembly has a variable volume cavity, the piston assembly is rotatably arranged in the cylinder sleeve, and the rotating shaft is drivingly connected with the piston assembly to change the volume of the variable volume cavity; wherein, a liquid inlet channel and a liquid discharge channel are arranged on the cylinder sleeve, the liquid inlet channel is communicated with the variable volume cavity and conveys refrigerant into the variable volume cavity, and the liquid discharge channel is communicated with the variable volume cavity and discharges the refrigerant in the variable volume cavity through the liquid discharge channel; at least one of the liquid discharge start position and the liquid discharge end position of the liquid discharge channel is provided with a liquid discharge tail groove to increase the communication area between the inner circle of the cylinder sleeve and the external high-pressure refrigerant.

[0007] Furthermore, the liquid drainage tail groove extends along the circumferential direction of the cylinder liner for a first preset distance to form a liquid drainage tail groove with an arc-shaped cross-section, and the radius of curvature of the arc where the liquid drainage tail groove is located is smaller than the radius of curvature of the arc where the liquid drainage channel is located.

[0008] Furthermore, the height L of the cylinder liner in its axial direction, the height L1 of the liquid drainage channel in the axial direction of the cylinder liner, and the height L2 of the liquid drainage tail groove in the axial direction of the cylinder liner satisfy: L1 ≤ L2 ≤ 0.5L.

[0009] Furthermore, there is a first sealing angle θ1 between the liquid drainage start position of the liquid drainage channel and the outer wall surface of the piston assembly; and / or, there is a second sealing angle θ2 between the liquid drainage end position of the liquid drainage channel and the outer wall surface of the piston assembly.

[0010] Furthermore, the piston assembly has a piston sleeve, and the piston sleeve is rotatably arranged in the cylinder liner. When the rotation angle of the piston sleeve is θ1, the external high-pressure refrigerant is communicated with the liquid drainage tail groove; when the rotation angle of the piston sleeve is 180° - θ2, the external high-pressure refrigerant is disconnected from the liquid drainage tail groove.

[0011] Furthermore, the liquid inlet channel extends along the circumferential direction of the inner wall surface of the cylinder liner for a second preset distance to form an arc-shaped liquid inlet channel, and there is a third sealing angle α between at least one of the liquid suction start position and the liquid suction end position of the liquid inlet channel and the outer wall surface of the piston assembly; where the first sealing angle θ1 and the third sealing angle α satisfy: 0° ≤ θ1 ≤ α; and / or, the second sealing angle θ2 and the third sealing angle α satisfy: 0° ≤ θ2 ≤ α°.

[0012] Furthermore, the value range of the first sealing angle θ1 is 0 ≤ θ1 ≤ 10°; and / or, the value range of the second sealing angle θ2 is 0 ≤ θ2 ≤ 10°.

[0013] Furthermore, there are two liquid drainage channels, and the two liquid drainage channels are arranged at intervals along the axial direction of the cylinder liner. The liquid drainage start position and the liquid drainage end position of each liquid drainage channel both have a liquid drainage tail groove. Among them, the two liquid drainage tail grooves are not connected, and at least one of the two liquid drainage tail grooves penetrates the axial end face of the cylinder liner; or, the two liquid drainage tail grooves are not connected, and neither of the two liquid drainage tail grooves penetrates the axial end face of the cylinder liner.

[0014] Furthermore, there are two liquid drainage channels, and the two liquid drainage channels are arranged at intervals along the axial direction of the cylinder liner. The liquid drainage start position and the liquid drainage end position of each liquid drainage channel both have a liquid drainage tail groove. Among them, the two liquid drainage tail grooves are connected, and at least one of the two liquid drainage tail grooves penetrates the axial end face of the cylinder liner; or, the two liquid drainage tail grooves are connected, and neither of the two liquid drainage tail grooves penetrates the axial end face of the cylinder liner.

[0015] According to another aspect of the present utility model, there is provided a heat exchange device, including a rotary cylinder pump, and the rotary cylinder pump is the above-mentioned rotary cylinder pump.

[0016] Applying the technical solution of the present utility model, there is provided a rotary cylinder pump, including a rotating shaft, a cylinder sleeve and a piston assembly. Among them, the rotating shaft is eccentrically arranged with the cylinder sleeve and the eccentric distance is fixed; the piston assembly has a variable volume chamber, the piston assembly is rotatably arranged in the cylinder sleeve, and the rotating shaft is drivingly connected with the piston assembly to change the volume of the variable volume chamber; a liquid inlet channel and a liquid discharge channel are arranged on the cylinder sleeve, the liquid inlet channel is communicated with the variable volume chamber and conveys refrigerant into the variable volume chamber, and the liquid discharge channel is communicated with the variable volume chamber and discharges the refrigerant in the variable volume chamber from the liquid discharge channel; at least one of the liquid discharge start position and the liquid discharge end position of the liquid discharge channel is provided with a liquid discharge tail groove to increase the communication area between the inner circle of the cylinder sleeve and the external high-pressure refrigerant.

[0017] By providing at least one of the liquid discharge start position and the liquid discharge end position of the liquid discharge channel with a liquid discharge tail groove, the communication area between the inner circle of the cylinder sleeve and the external high-pressure refrigerant is increased, the channel area of the liquid discharge channel is further increased, and thus the purpose of reducing the liquid discharge resistance of the liquid discharge channel is achieved, the instantaneous pressure during the liquid discharge process of the liquid discharge channel is reduced, and over-compression is reduced, which is beneficial to improving the performance and reliability of the rotary cylinder pump. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The schematic drawings of the specification forming a part of this application are used to provide a further understanding of the present utility model. The schematic embodiments of the present utility model and their descriptions are used to explain the present utility model and do not constitute an improper limitation to the present utility model. In the drawings:

[0019] Figure 1 The schematic diagram of the cylinder sleeve of a rotary cylinder pump according to an optional embodiment of the present utility model is shown;

[0020] Figure 2 Shown Figure 1 The cross-sectional structure schematic diagram of the cylinder sleeve in

[0021] Figure 3 The structural schematic diagram of the rotary cylinder pump from a top view perspective according to an optional embodiment of the present utility model is shown. In this figure, the third sealing angle α is shown;

[0022] Figure 4 The structural schematic diagram of the rotary cylinder pump from a top view perspective according to an optional embodiment of the present utility model is shown. In this figure, the first sealing angle θ1 and the second sealing angle θ2 are shown;

[0023] Figure 5 The schematic diagram of the cylinder sleeve of the rotary cylinder pump according to Embodiment 1 of the present utility model is shown;

[0024] Figure 6 Shows a schematic diagram of the cylinder liner of a rotary cylinder pump according to Embodiment 2 of the present utility model;

[0025] Figure 7 Shows a schematic diagram of the cylinder liner of a rotary cylinder pump according to Embodiment 3 of the present utility model;

[0026] Figure 8 Shows a schematic diagram of the cylinder liner of a rotary cylinder pump according to Embodiment 4 of the present utility model;

[0027] Figure 9 Shows a schematic diagram of the cylinder liner of a rotary cylinder pump according to Embodiment 5 of the present utility model;

[0028] Figure 10 Shows a schematic diagram of the cylinder liner of a rotary cylinder pump according to Embodiment 6 of the present utility model.

[0029] Among them, the above-mentioned drawings include the following reference numerals:

[0030] 10, rotating shaft;

[0031] 20, cylinder liner; 21, liquid inlet channel; 22, liquid discharge channel; 23, liquid discharge tail groove;

[0032] 30, piston assembly; 31, variable volume chamber; 32, piston sleeve; 33, piston. Specific embodiments

[0033] Next, the technical solutions in the embodiments of the present utility model will be clearly and completely described in conjunction with the drawings in the embodiments of the present utility model. Obviously, the described embodiments are only a part of the embodiments of the present utility model, rather than all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and in no way restricts the present utility model and its application or use. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present utility model without creative efforts fall within the scope of protection of the present utility model.

[0034] To solve the problem that in the prior art, the fluorine pump has a large liquid discharge resistance at both the initial stage and the end stage of liquid discharge due to the reduction of the radial liquid discharge area of the cylinder, seriously affecting the performance of the fluorine pump, the present utility model provides a rotary cylinder pump and a heat exchange device. Among them, the heat exchange device includes a rotary cylinder pump, and the rotary cylinder pump is the rotary cylinder pump described above and below.

[0035] Such as Figures 1 to 4As shown in the figure, the rotary cylinder pump includes a rotating shaft 10, a cylinder liner 20 and a piston assembly 30. The rotating shaft 10 is eccentrically arranged with respect to the cylinder liner 20 and the eccentric distance is fixed. The piston assembly 30 has a variable volume chamber 31. The piston assembly 30 is rotatably arranged in the cylinder liner 20, and the rotating shaft 10 is drivingly connected to the piston assembly 30 to change the volume of the variable volume chamber 31. Among them, a liquid inlet passage 21 and a liquid discharge passage 22 are provided on the cylinder liner 20. The liquid inlet passage 21 is connected to the variable volume chamber 31 and conveys refrigerant into the variable volume chamber 31. The liquid discharge passage 22 is connected to the variable volume chamber 31 and discharges the refrigerant in the variable volume chamber 31 from the liquid discharge passage 22. At least one of the liquid discharge start position and the liquid discharge end position of the liquid discharge passage 22 is provided with a liquid discharge tail groove 23 to increase the communication area between the inner circle of the cylinder liner 20 and the external high-pressure refrigerant.

[0036] Applying the technical solution of the present utility model, a rotary cylinder pump is provided, including a rotating shaft 10, a cylinder liner 20 and a piston assembly 30. Among them, the rotating shaft 10 is eccentrically arranged with respect to the cylinder liner 20 and the eccentric distance is fixed. The piston assembly 30 has a variable volume chamber 31. The piston assembly 30 is rotatably arranged in the cylinder liner 20, and the rotating shaft 10 is drivingly connected to the piston assembly 30 to change the volume of the variable volume chamber 31. A liquid inlet passage 21 and a liquid discharge passage 22 are provided on the cylinder liner 20. The liquid inlet passage 21 is connected to the variable volume chamber 31 and conveys refrigerant into the variable volume chamber 31. The liquid discharge passage 22 is connected to the variable volume chamber 31 and discharges the refrigerant in the variable volume chamber 31 from the liquid discharge passage 22. At least one of the liquid discharge start position and the liquid discharge end position of the liquid discharge passage 22 is provided with a liquid discharge tail groove 23 to increase the communication area between the inner circle of the cylinder liner 20 and the external high-pressure refrigerant.

[0037] By providing a liquid discharge tail groove 23 at least at one of the liquid discharge start position and the liquid discharge end position of the liquid discharge passage 22, the communication area between the inner circle of the cylinder liner 20 and the external high-pressure refrigerant is increased, the channel area of the liquid discharge passage 22 is further enlarged, and the purpose of reducing the liquid discharge resistance of the liquid discharge passage 22 is achieved, the instantaneous pressure during the liquid discharge process of the liquid discharge passage 22 is reduced, and over-compression is reduced, which is beneficial to improving the performance and reliability of the rotary cylinder pump.

[0038] It should be noted that in this application, as Figure 4 shown, the liquid discharge tail groove 23 extends along the circumferential direction of the cylinder liner 20 for a first preset distance to form a liquid discharge tail groove 23 with an arc-shaped cross-section. The radius of curvature of the arc where the liquid discharge tail groove 23 is located is smaller than the radius of curvature of the arc where the liquid discharge passage 22 is located. In this way, the liquid discharge reliability and the liquid discharge smoothness of the liquid discharge passage 22 are ensured.

[0039] As Figure 2As shown, the height L of the cylinder liner 20 in its axial direction, the height L1 of the liquid discharge channel 22 in the axial direction of the cylinder liner 20, and the height L2 of the liquid discharge tail groove 23 in the axial direction of the cylinder liner 20 satisfy: L1 ≤ L2 ≤ 0.5L. In this way, by reasonably optimizing the relationship among the height L of the cylinder liner 20 in its axial direction, the height L1 of the liquid discharge channel 22 in the axial direction of the cylinder liner 20, and the height L2 of the liquid discharge tail groove 23 in the axial direction of the cylinder liner 20, it is ensured that the communication area between the inner circle of the cylinder liner 20 and the external high-pressure refrigerant can be increased as much as possible, so that the channel area of the liquid discharge channel 22 is increased, and further the purpose of reducing the liquid discharge resistance of the liquid discharge channel 22 is achieved, the situation of insufficient liquid discharge in the liquid discharge channel 22 is alleviated, and the performance and reliability of the rotary cylinder pump are greatly improved.

[0040] As Figure 4 shown, there is a first sealing angle θ1 between the liquid discharge start position of the liquid discharge channel 22 and the outer wall surface of the piston assembly 30; and / or, there is a second sealing angle θ2 between the liquid discharge end position of the liquid discharge channel 22 and the outer wall surface of the piston assembly 30.

[0041] Further, the piston assembly 30 has a piston sleeve 32, and the piston sleeve 32 is rotatably arranged in the cylinder liner 20. Among them, when the rotation angle of the piston sleeve 32 is θ1, the external high-pressure refrigerant is communicated with the liquid discharge tail groove 23; when the rotation angle of the piston sleeve 32 is 180° - θ2, the external high-pressure refrigerant is disconnected from the liquid discharge tail groove 23.

[0042] As Figure 3 shown, the piston assembly 30 has two limiting channels, and the two limiting channels are sequentially arranged along the axial direction of the rotating shaft 10, and the extending direction of the limiting channels is perpendicular to the axial direction of the rotating shaft 10; the piston 33 has through holes, there are two pistons 33, and the two eccentric parts of the rotating shaft 10 correspondingly extend into the two through holes of the two pistons 33, and the two pistons 33 are correspondingly slidably arranged in the two limiting channels and form a variable volume chamber 31. The variable volume chamber 31 is located in the sliding direction of the piston 33. The rotating shaft 10 rotates to drive the piston 33 to reciprocate in the limiting channel while interacting with the piston assembly 30, so that the piston assembly 30 and the piston 33 rotate in the cylinder liner 20.

[0043] As Figure 3 and 4 shown, the liquid inlet channel 21 extends along the circumferential direction of the inner wall surface of the cylinder liner 20 for a second preset distance to form an arc-shaped liquid inlet channel 21. There is a third sealing angle α between at least one of the liquid suction start position and the liquid suction end position of the liquid inlet channel 21 and the outer wall surface of the piston assembly 30; among them, the first sealing angle θ1 and the third sealing angle α satisfy: 0° ≤ θ1 ≤ α; and / or, the second sealing angle θ2 and the third sealing angle α satisfy: 0° ≤ θ2 ≤ α°.

[0044] Furthermore, the value range of the first sealing angle θ1 is 0≤θ1≤10°; and / or, the value range of the second sealing angle θ2 is 0≤θ2≤10°.

[0045] It should be noted that in this application, there are two drain channels 22, and the two drain channels 22 are arranged at intervals along the axial direction of the cylinder liner 20. Drain tail grooves 23 are provided at both the drain start position and the drain end position of each drain channel 22. Among them, the two drain tail grooves 23 are not connected, and at least one of the two drain tail grooves 23 penetrates the axial end face of the cylinder liner 20; or, the two drain tail grooves 23 are not connected, and neither of the two drain tail grooves 23 penetrates the axial end face of the cylinder liner 20.

[0046] Embodiment 1

[0047] As Figure 5 shown, the two drain tail grooves 23 are not connected, and both of the two drain tail grooves 23 penetrate the axial end face of the cylinder liner 20.

[0048] Embodiment 2

[0049] As Figure 6 shown, the two drain tail grooves 23 are not connected, and one of the two drain tail grooves 23 penetrates the axial end face of the cylinder liner 20.

[0050] Embodiment 3

[0051] As Figure 7 shown, the two drain tail grooves 23 are not connected, and neither of the two drain tail grooves 23 penetrates the axial end face of the cylinder liner 20.

[0052] It should be noted that in this application, there are two drain channels 22, and the two drain channels 22 are arranged at intervals along the axial direction of the cylinder liner 20. Drain tail grooves 23 are provided at both the drain start position and the drain end position of each drain channel 22. Among them, the two drain tail grooves 23 are connected, and at least one of the two drain tail grooves 23 penetrates the axial end face of the cylinder liner 20; or, the two drain tail grooves 23 are connected, and neither of the two drain tail grooves 23 penetrates the axial end face of the cylinder liner 20.

[0053] Embodiment 4

[0054] As Figure 8 shown, the two drain tail grooves 23 are connected, and both of the two drain tail grooves 23 penetrate the axial end face of the cylinder liner 20.

[0055] Embodiment 5

[0056] As Figure 9 shown, the two drain tail grooves 23 are connected, and one of the two drain tail grooves 23 penetrates the axial end face of the cylinder liner 20.

[0057] Embodiment VI

[0058] As Figure 10 shown, two liquid discharge tail grooves 23 are connected, and neither of the two liquid discharge tail grooves 23 penetrates the axial end faces of the cylinder liner 20.

[0059] Applying the technical solution of the present utility model, a rotary cylinder pump is provided, which includes a rotating shaft 10, a cylinder liner 20 and a piston assembly 30. Among them, the rotating shaft 10 and the cylinder liner 20 are eccentrically arranged with a fixed eccentric distance; the piston assembly 30 has a variable volume chamber 31, the piston assembly 30 is rotatably arranged in the cylinder liner 20, and the rotating shaft 10 is drivingly connected to the piston assembly 30 to change the volume of the variable volume chamber 31; a liquid inlet channel 21 and a liquid discharge channel 22 are arranged on the cylinder liner 20, the liquid inlet channel 21 is connected to the variable volume chamber 31 and conveys refrigerant into the variable volume chamber 31, and the liquid discharge channel 22 is connected to the variable volume chamber 31 and discharges the refrigerant in the variable volume chamber 31 through the liquid discharge channel 22; at least one of the liquid discharge start position and the liquid discharge end position of the liquid discharge channel 22 is provided with a liquid discharge tail groove 23 to increase the communication area between the inner circle of the cylinder liner 20 and the external high-pressure refrigerant.

[0060] By providing at least one of the liquid discharge start position and the liquid discharge end position of the liquid discharge channel 22 with a liquid discharge tail groove 23, the communication area between the inner circle of the cylinder liner 20 and the external high-pressure refrigerant is increased, the channel area of the liquid discharge channel 22 is further enlarged, and thus the purpose of reducing the liquid discharge resistance of the liquid discharge channel 22 is achieved, the instantaneous pressure during the liquid discharge process of the liquid discharge channel 22 is reduced, and over-compression is reduced, which is beneficial to improving the performance and reliability of the rotary cylinder pump.

[0061] It should be noted that the terms used here are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used here, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, they indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0062] Unless otherwise specifically stated, the relative arrangements, numerical expressions, and numerical values of the components and steps set forth in these embodiments do not limit the scope of the present utility model. At the same time, it should be understood that, for the sake of convenience in description, the dimensions of the various parts shown in the drawings are not drawn in actual proportional relationships. Technologies, methods, and devices known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, the said technologies, methods, and devices should be regarded as part of the authorization specification. In all the examples shown and discussed herein, any specific values should be construed as merely exemplary and not as a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following drawings, and thus, once an item is defined in one drawing, further discussion thereof in subsequent drawings is not required.

[0063] For the sake of convenience in description, spatial relative terms such as "above", "over", "on the upper surface", "upper" etc. may be used herein to describe the spatial positional relationship of one device or feature shown in the figures with other devices or features. It should be understood that the spatial relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures of the device. For example, if the device in the figures is inverted, the device described as "above" or "over" other devices or structures will then be positioned "below" or "beneath" other devices or structures. Thus, the exemplary term "above" can include both the orientations of "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and corresponding interpretations will be made for the spatial relative descriptions used herein.

[0064] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular forms are also intended to include the plural forms. In addition, it should also be understood that when the terms "comprise" and / or "include" are used in this specification, they specify the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0065] It should be noted that the terms "first", "second", etc. in the specification, claims, and above-mentioned drawings of the present application are used to distinguish similar objects and do not necessarily have to be 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 the present application described herein can be implemented in an order different from those illustrated or described herein.

[0066] The above are only the preferred embodiments of the present utility model and are not intended to limit the present utility model. For those skilled in the art, the present utility model may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present utility model shall be included within the protection scope of the present utility model.

Claims

1. A rotary cylinder pump, characterized in that: include: Rotating shaft (10); The cylinder sleeve (20), the rotating shaft (10) and the cylinder sleeve (20) are eccentrically arranged with a fixed eccentric distance; A piston assembly (30), the piston assembly (30) having a variable volume chamber (31), the piston assembly (30) being rotatably disposed in the cylinder sleeve (20), and the rotating shaft (10) being drivingly connected to the piston assembly (30) to change the volume of the variable volume chamber (31); The cylinder sleeve (20) is provided with a liquid inlet channel (21) and a liquid discharge channel (22), the liquid inlet channel (21) is communicated with the variable volume chamber (31) and transports refrigerant into the variable volume chamber (31), and the liquid discharge channel (22) is communicated with the variable volume chamber (31) and discharges the refrigerant in the variable volume chamber (31) through the liquid discharge channel (22); A drainage tail groove (23) is provided at least at one of the drainage start position and the drainage end position of the drainage channel (22) to increase the communication area between the inner circle of the cylinder sleeve (20) and the external high-pressure refrigerant.

2. The rotary cylinder pump according to claim 1, characterized in that The drainage tail groove (23) extends a first preset distance along the circumference of the cylinder sleeve (20) to form a drainage tail groove (23) with an arc-shaped cross section, and the curvature radius of the arc where the drainage tail groove (23) is located is smaller than the curvature radius of the arc where the drainage channel (22) is located.

3. The rotary cylinder pump according to claim 1, characterized in that The height L of the cylinder liner (20) in the axial direction, the height L1 of the drainage channel (22) in the axial direction of the cylinder liner (20), and the height L2 of the drainage tail groove (23) in the axial direction of the cylinder liner (20) satisfy the following conditions: L1≤L2≤0.5L.

4. The rotary cylinder pump according to claim 2, characterized in that: A first sealing angle θ1 is formed between the discharge starting position of the discharge channel (22) and the outer wall surface of the piston assembly (30); and / or, A second sealing angle θ2 is formed between the discharge end position of the discharge channel (22) and the outer wall surface of the piston assembly (30).

5. The rotary cylinder pump according to claim 4, characterized in that: The piston assembly (30) has a piston sleeve (32) which is rotatably arranged in the cylinder sleeve (20), wherein: When the rotation angle of the piston sleeve (32) is θ1, the external high-pressure refrigerant is communicated with the liquid discharge tail groove (23); When the rotation angle of the piston sleeve (32) is 180°-θ2, the external high-pressure refrigerant is disconnected from the liquid discharge tail groove (23).

6. The rotary cylinder pump according to claim 4, characterized in that The liquid inlet channel (21) extends a second preset distance along the circumference of the inner wall surface of the cylinder sleeve (20) to form an arc-shaped liquid inlet channel (21), and a third sealing angle α is formed between at least one of a liquid suction starting position and a liquid suction ending position of the liquid inlet channel (21) and the outer wall surface of the piston assembly (30); Wherein, the first sealing angle θ1 and the third sealing angle α satisfy the following conditions: 0°≤θ1≤α; and / or, The second sealing angle θ2 and the third sealing angle α satisfy the following condition: 0°≤θ2≤α°.

7. The rotary cylinder pump according to claim 6, characterized in that The first sealing angle θ1 has a value range of 0≤θ1≤10°; and / or, The value range of the second sealing angle θ2 is 0≤θ2≤10°.

8. The rotary cylinder pump according to claim 1, characterized in that There are two drainage channels (22), and the two drainage channels (22) are spaced apart along the axial direction of the cylinder sleeve (20). Each drainage channel (22) has a drainage tail groove (23) at the drainage start position and the drainage end position, wherein: The two drainage tail grooves (23) are not connected, and at least one of the two drainage tail grooves (23) passes through the axial end surface of the cylinder liner (20); or, The two liquid discharge tail grooves (23) are not connected, and both of the liquid discharge tail grooves (23) do not penetrate the axial end surface of the cylinder sleeve (20).

9. The rotary cylinder pump according to claim 1, characterized in that There are two drainage channels (22), and the two drainage channels (22) are spaced apart along the axial direction of the cylinder sleeve (20). Each drainage channel (22) has a drainage tail groove (23) at the drainage start position and the drainage end position, wherein: The two drainage tail grooves (23) are connected, and at least one of the two drainage tail grooves (23) passes through the axial end surface of the cylinder liner (20); or, The two liquid discharge tail grooves (23) are connected, and neither of the two liquid discharge tail grooves (23) passes through the axial end surface of the cylinder sleeve (20).

10. A heat exchange device, characterized in that: The invention comprises a rotary cylinder pump, wherein the rotary cylinder pump is the rotary cylinder pump according to any one of claims 1 to 9.

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