Rotary pump and heat exchange device

Abstract

The utility model provides a kind of rotary cylinder pump and heat exchange equipment, rotary cylinder pump includes rotating shaft, cylinder sleeve, piston sleeve and piston, rotating shaft lubricating oil channel is connected with oil pool, rotating shaft has two eccentric parts;Rotating shaft is eccentric with cylinder sleeve and the eccentric distance is fixed;Piston sleeve is rotatably arranged in cylinder sleeve, the extension direction of two limit passages of piston sleeve is perpendicular to the axial direction of rotating shaft;Two eccentric parts are correspondingly inserted into the two through holes of two pistons, two pistons are correspondingly slidably arranged in two limit passages and form variable volume chamber, variable volume chamber is located in the sliding direction of piston;Piston sleeve has oil hole, the communication hole of rotating shaft is used to connect lubricating oil channel and oil hole.The utility model solves the problem that the fluorine pump in the prior art produces friction power consumption, reduces the energy efficiency of fluorine pump, and even reduces the service life of piston sleeve and cylinder sleeve during operation, that the outer peripheral surface of piston sleeve and the inner peripheral surface of cylinder sleeve are rubbed against each other.

Description

Technical Field

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

[0002] With the development of society, the power consumption of data centers is increasing year by year, resulting in huge power consumption. Data center air conditioning is an important component of data centers, accounting for 40% of the power consumption of data centers, and the application of its energy-saving technology is of great significance.

[0003] Data center air conditioning systems are devices used to cool the electrical components of data centers. They need to provide continuous cooling year-round to ensure the indoor temperature remains within a certain range. Most existing data center air conditioning systems use compression refrigeration technology, relying on this system for cooling in both summer and winter. When the ambient temperature is high, existing compression refrigeration technology meets performance and energy efficiency requirements; however, when the outdoor ambient temperature is significantly lower than the indoor temperature, the most economical and energy-efficient cooling method is to use the low outdoor temperature to cool the indoor temperature. The industry has been exploring a low-temperature cooling mode that can fully utilize the low outdoor temperature and is highly economical. In recent years, a refrigerant pump-compressor dual-cycle system has been proposed. This system uses the existing compression refrigeration mode during hot seasons; during cold seasons, a low-power refrigerant pump replaces the high-power compressor as the power source to complete the refrigeration cycle, thereby achieving energy savings.

[0004] However, in the existing technology, during the operation of the fluorine pump, the piston sleeve rotates at high speed inside the cylinder liner, causing friction between the outer circumferential surface of the piston sleeve and the inner circumferential surface of the cylinder liner, generating frictional power consumption, reducing the energy efficiency of the fluorine pump, and even reducing the service life of the piston sleeve and cylinder liner. Utility Model Content

[0005] The main purpose of this utility model is to provide a rotary cylinder pump and heat exchange equipment to solve the problem that in the prior art, during the operation of a fluorine pump, the piston sleeve rotates at high speed inside the cylinder sleeve, causing friction between the outer circumferential surface of the piston sleeve and the inner circumferential surface of the cylinder sleeve, generating frictional power consumption, reducing the energy efficiency of the fluorine pump, and even reducing the service life of the piston sleeve and cylinder sleeve.

[0006] To achieve the above objectives, according to one aspect of the present invention, a rotary cylinder pump is provided, comprising a rotating shaft, a cylinder liner, a piston sleeve, and a piston. The rotating shaft has a lubricating oil passage extending axially along the shaft and penetrating one axial end of the shaft to connect the lubricating oil passage to an oil sump. The rotating shaft also has two eccentric portions along its axial direction. The rotating shaft and the cylinder liner are eccentrically positioned with a fixed eccentric distance. The piston sleeve is rotatably disposed within the cylinder liner and has two limiting channels, both of which are sequentially arranged axially along the rotating shaft, with the extending direction of the limiting channels perpendicular to the axial direction of the rotating shaft. The piston has a through hole, and there are two pistons. The eccentric part extends into the two through holes of the two pistons. The two pistons are slidably arranged in the two limiting channels and form a variable volume cavity. The variable volume cavity is located in the sliding direction of the piston. The rotating shaft rotates to drive the piston to slide back and forth in the limiting channel while interacting with the piston sleeve, so that the piston sleeve and the piston rotate in the cylinder liner. The piston sleeve has an oil passage hole that passes through the inner and outer circumferential surfaces of the piston sleeve. The rotating shaft also has a connecting hole that connects the lubricating oil passage and the oil passage hole, so that the refrigeration oil in the oil sump flows into the space between the outer circumferential surface of the piston sleeve and the inner circumferential surface of the cylinder liner in sequence through the lubricating oil passage, the connecting hole, and the oil passage hole.

[0007] Furthermore, the piston sleeve has a central hole, through which two limiting channels are connected, and the diameter of the central hole is larger than the diameter of the shaft body portion of the rotating shaft; the oil passage hole extends radially along the piston sleeve and penetrates the hole wall of the central hole, and the connecting hole extends radially along the rotating shaft and penetrates the shaft body portion located in the central hole.

[0008] Furthermore, the cylinder liner has a liquid inlet channel that extends radially and penetrates the outer circumferential surface of the cylinder liner. The inner wall of the cylinder liner also has two liquid suction chambers, which are spaced apart along the axial direction of the cylinder liner. The cylinder liner also has a through hole that penetrates the two end faces of the cylinder liner along the axial direction and is used to connect the two liquid suction chambers with the liquid inlet channel, so that the refrigerant flows sequentially through the liquid inlet channel, the through hole, and the two liquid suction chambers to the corresponding two variable volume chambers. The diameter D1 of the oil passage hole, the first sealing height H1 of the oil passage hole and the liquid suction chamber in the axial direction of the cylinder liner, and the first cavity opening distance H2 of the two liquid suction chambers communicating with the corresponding two variable volume chambers in the axial direction of the cylinder liner satisfy the following: 0.1mm≤H1≤H2-D1-0.1mm.

[0009] Furthermore, the cylinder liner has two drainage channels, which are spaced apart along the axial direction of the cylinder liner and extend radially through the outer circumference of the cylinder liner. The two drainage channels are not connected. The diameter D1 of the oil passage hole, the second sealing height H3 of the oil passage hole and drainage channel in the axial direction of the cylinder liner, and the distance H4 between the second cavity openings of the two drainage channels and the corresponding two variable volume cavities in the axial direction of the cylinder liner satisfy the following: 0.1mm≤H3≤H4-D1-0.1mm.

[0010] Furthermore, the diameter D1 of the oil passage hole, the third sealing height H5 of the oil passage hole and the limiting channel in the axial direction of the piston sleeve, and the axial distance H6 between the two limiting channels in the piston sleeve satisfy the following: 0.1mm≤H5≤H6-D1-0.1mm.

[0011] Furthermore, the diameter D1 of the oil passage hole satisfies: 0.5mm≤D1≤5mm.

[0012] Furthermore, the cross-section of the oil passage can be circular, elliptical, or polygonal.

[0013] Furthermore, the number of oil passage holes is one or more; wherein, when there are multiple oil passage holes, at least two of the multiple oil passage holes are at different heights in the axial direction of the piston sleeve; or, the multiple oil passage holes are at the same height in the axial direction of the piston sleeve.

[0014] 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 limiting difference of a second included angle B between the extending directions of the two limiting channels, wherein the first included angle A is twice the second included angle B.

[0015] Furthermore, there are two oil passages, and there is a limiting difference of a third included angle C between the extending directions of the two oil passages. The third included angle C is equal to the second included angle B.

[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] This utility model provides a rotary cylinder pump, including a rotating shaft, a cylinder liner, a piston sleeve, and a piston. The rotating shaft has a lubricating oil passage extending axially along the shaft and penetrating one axial end to connect with an oil sump. The rotating shaft also has two eccentric portions along its axial direction. The rotating shaft and cylinder liner are eccentrically positioned with a fixed eccentricity. The piston sleeve is rotatably mounted within the cylinder liner and has two limiting channels, both sequentially arranged axially along the rotating shaft, with the extending direction of the limiting channels perpendicular to the axial direction of the rotating shaft. The piston has a through hole, and there are two pistons. The two eccentric portions are aligned with... It should extend into the two through holes of the two pistons. The two pistons are correspondingly slidably arranged in the two limiting channels and form a variable volume cavity. The variable volume cavity is located in the sliding direction of the piston. The rotating shaft rotates to drive the piston to slide back and forth in the limiting channel while interacting with the piston sleeve, so that the piston sleeve and the piston rotate in the cylinder liner. The piston sleeve has an oil passage hole that passes through the inner and outer circumferential surfaces of the piston sleeve. The rotating shaft also has a connecting hole for connecting the lubricating oil passage and the oil passage hole, so that the refrigeration oil in the oil sump flows into the space between the outer circumferential surface of the piston sleeve and the inner circumferential surface of the cylinder liner in sequence through the lubricating oil passage, the connecting hole, and the oil passage hole.

[0018] By setting lubricating oil channels and connecting holes on the rotating shaft, and oil passage holes on the piston sleeve, during the rotation of the rotating shaft, the refrigerant oil drawn into the lubricating oil channels is transported sequentially through the connecting holes and oil passage holes to the outer circumferential surface of the piston sleeve and the inner circumferential surface of the cylinder sleeve by centrifugal force. This lubricates the contact surfaces between the two, reduces the frictional power consumption between them, and helps to improve the energy efficiency of the rotary cylinder pump. Attached Figure Description

[0019] The accompanying drawings, which form part of this application, are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an undue limitation of the present invention. In the drawings:

[0020] Figure 1 A cross-sectional structural schematic diagram of a rotary cylinder pump according to an alternative embodiment of the present invention is shown;

[0021] Figure 2 An exploded view of a rotary pump according to an alternative embodiment of the present invention is shown.

[0022] Figure 3 It shows Figure 1 A cross-sectional view of the rotary cylinder pump from another perspective;

[0023] Figure 4 It shows Figure 2 A schematic diagram of the cylinder liner of the rotary pump.

[0024] Figure 5It shows Figure 4 Schematic diagram of the cross-sectional structure at DD in the diagram;

[0025] Figure 6 It shows Figure 1 A cross-sectional view of the cylinder liner and piston liner of the rotary pump in the assembled state.

[0026] Figure 7 It shows Figure 2 A schematic diagram of the piston sleeve in a rotary pump.

[0027] Figure 8 It shows Figure 7 A structural schematic diagram of the piston sleeve from another perspective.

[0028] The above figures include the following reference numerals:

[0029] 10. Shaft; 11. Lubricating oil passage; 12. Eccentric part; 13. Connecting hole;

[0030] 20. Cylinder liner; 21. Liquid inlet channel; 22. Liquid suction chamber; 23. Liquid discharge channel; 24. Through hole;

[0031] 30. Piston sleeve; 31. Limiting channel; 311. Variable volume cavity; 32. Oil passage; 33. Center hole;

[0032] 40. Piston; 41. Through hole;

[0033] 51. Upper flange; 52. Lower flange. Detailed Implementation

[0034] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, 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 utility model or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of the present utility model without creative effort are within the scope of protection of the present utility model.

[0035] To address the problem in existing refrigerant pumps where the piston sleeve rotates at high speed within the cylinder liner during operation, causing friction between the outer circumferential surface of the piston sleeve and the inner circumferential surface of the cylinder liner, resulting in frictional power consumption, reduced pump efficiency, and even shortened service life of the piston sleeve and cylinder liner, this invention provides a rotary cylinder pump and a heat exchange device. The heat exchange device includes a rotary cylinder pump, which is the rotary cylinder pump described above and below.

[0036] like Figures 1 to 8As shown, the rotary pump includes a shaft 10, a cylinder liner 20, a piston sleeve 30, and a piston 40. The shaft 10 has a lubrication passage 11, which extends axially along the shaft 10 and passes through one axial end of the shaft 10, allowing the lubrication passage 11 to communicate with the oil sump. The shaft 10 also has two eccentric portions 12 along its axial direction. The shaft 10 is eccentrically positioned to the cylinder liner 20 with a fixed eccentricity. The piston sleeve 30 is rotatably mounted within the cylinder liner 20 and has two limiting channels 31, both of which are sequentially arranged axially along the shaft 10, with the extending direction of the limiting channels 31 perpendicular to the axial direction of the shaft 10. The piston 40 has a through hole 41, and there are two pistons 40. The two eccentric portions 12 extend into the two pistons 40 respectively. Within each through hole 41, two pistons 40 are slidably disposed within two limiting channels 31, forming a variable volume cavity 311. The variable volume cavity 311 is located in the sliding direction of the pistons 40. The rotating shaft 10 rotates to drive the pistons 40 to slide back and forth within the limiting channels 31 while interacting with the piston sleeve 30, so that the piston sleeve 30 and the pistons 40 rotate within the cylinder liner 20. The piston sleeve 30 has an oil passage 32 that passes through the inner and outer circumferential surfaces of the piston sleeve 30. The rotating shaft 10 also has a connecting hole 13, which is used to connect the lubricating oil passage 11 and the oil passage 32, so that the refrigeration oil in the oil sump flows sequentially through the lubricating oil passage 11, the connecting hole 13, and the oil passage 32 between the outer circumferential surface of the piston sleeve 30 and the inner circumferential surface of the cylinder liner 20.

[0037] The present invention provides a rotary cylinder pump, comprising a rotating shaft 10, a cylinder liner 20, a piston sleeve 30, and a piston 40. The rotating shaft 10 has a lubrication passage 11 extending axially along the rotating shaft 10 and penetrating one axial end of the rotating shaft 10, thereby communicating with an oil sump. The rotating shaft 10 also has two eccentric portions 12 along its axial direction. The rotating shaft 10 is eccentrically positioned to the cylinder liner 20 with a fixed eccentricity. The piston sleeve 30 is rotatably disposed within the cylinder liner 20 and has two limiting channels 31, both of which are sequentially arranged axially along the rotating shaft 10, with the extending direction of the limiting channels 31 perpendicular to the axial direction of the rotating shaft 10. The piston 40 has a through hole 41, and there are two pistons 40, with the two eccentric portions 12 correspondingly extending into them. The two pistons 40 are slidably disposed in the two through holes 41 of the two pistons 40 and in the two limiting channels 31 to form a variable volume cavity 311. The variable volume cavity 311 is located in the sliding direction of the pistons 40. The rotating shaft 10 rotates to drive the pistons 40 to slide back and forth in the limiting channels 31 and interact with the piston sleeve 30, so that the piston sleeve 30 and the pistons 40 rotate in the cylinder liner 20. The piston sleeve 30 has an oil passage 32 that passes through the inner and outer circumferential surfaces of the piston sleeve 30. The rotating shaft 10 also has a connecting hole 13 for connecting the lubricating oil passage 11 and the oil passage 32, so that the refrigeration oil in the oil sump flows into the space between the outer circumferential surface of the piston sleeve 30 and the inner circumferential surface of the cylinder liner 20 in sequence through the lubricating oil passage 11, the connecting hole 13, and the oil passage 32.

[0038] By providing a lubricating oil passage 11 and a connecting hole 13 on the rotating shaft 10, and an oil passage hole 32 on the piston sleeve 30, during the rotation of the rotating shaft 10, the refrigerant oil drawn into the lubricating oil passage 11 is transported sequentially through the connecting hole 13 and the oil passage hole 32 to the outer circumferential surface of the piston sleeve 30 and the inner circumferential surface of the cylinder liner 20 through centrifugal force. This lubricates the contact surfaces between the two, reduces the frictional power consumption between them, and helps to improve the energy efficiency of the rotary cylinder pump.

[0039] like Figure 1 , Figure 2 , Figure 7 As shown, the piston sleeve 30 has a central hole 33, through which two limiting channels 31 are connected, and the diameter of the central hole 33 is larger than the diameter of the shaft portion of the rotating shaft 10; the oil passage 32 extends radially along the piston sleeve 30 and penetrates the wall of the central hole 33, and the connecting hole 13 extends radially along the rotating shaft 10 and penetrates the shaft portion located within the central hole 33. This ensures reliable communication between the oil passage 32 and the lubricating oil passage 11 via the connecting hole 13.

[0040] like Figure 5 and Figure 6As shown, the cylinder liner 20 has a liquid inlet channel 21, which extends radially and penetrates the outer peripheral surface of the cylinder liner 20. The inner wall of the cylinder liner 20 also has two liquid suction chambers 22, which are spaced apart along the axial direction of the cylinder liner 20. The cylinder liner 20 also has a through hole 24, which penetrates the two end faces of the cylinder liner 20 along the axial direction. The through hole 24 is used to connect the two liquid suction chambers 22 with the liquid inlet channel 21, so that the refrigerant flows sequentially through the liquid inlet channel 21, the through hole 24, and the two liquid suction chambers 22 to the corresponding two variable volume chambers 311. The diameter D1 of the oil passage hole 32, the first sealing height H1 of the oil passage hole 32 and the liquid suction chamber 22 in the axial direction of the cylinder liner 20, and the first cavity opening distance H2 of the two liquid suction chambers 22 communicating with the corresponding two variable volume chambers 311 in the axial direction of the cylinder liner 20 satisfy the following: 0.1mm≤H1≤H2-D1-0.1mm. This ensures that the oil passage 32 does not connect with the liquid suction chamber 22 when it passes the liquid suction position, preventing leakage from the oil passage 32 and affecting the cooling capacity and performance of the rotary pump.

[0041] like Figure 5 and Figure 6 As shown, the cylinder liner 20 has two drain channels 23, which are spaced apart along the axial direction of the cylinder liner 20. Both drain channels 23 extend radially through the outer circumferential surface of the cylinder liner 20 and are not connected. The diameter D1 of the oil passage hole 32, the second sealing height H3 of the oil passage hole 32 and the drain channel 23 along the axial direction of the cylinder liner 20, and the distance H4 between the two drain channels 23 and the corresponding two variable volume cavities 311 along the axial direction of the cylinder liner 20 satisfy the following: 0.1mm ≤ H3 ≤ H4 - D1 - 0.1mm. This ensures that the oil passage hole 32 does not connect with the drain channel 23 when passing through the drain position, preventing leakage from the oil passage hole 32 and affecting the cooling capacity and performance of the rotary pump.

[0042] like Figure 8 As shown, the diameter D1 of the oil passage 32, the third sealing height H5 of the oil passage 32 and the limiting channel 31 in the axial direction of the piston sleeve 30, and the axial spacing H6 of the two limiting channels 31 in the piston sleeve 30 satisfy the following condition: 0.1mm ≤ H5 ≤ H6 - D1 - 0.1mm. This ensures that the oil passage 32 is not connected to the variable volume chamber 311, preventing high-pressure liquid from leaking directly from the oil passage 32 into the variable volume chamber 311, thus affecting the cooling capacity and performance of the rotary pump.

[0043] It should be noted that in this application, the diameter D1 of the oil passage 32 satisfies: 0.5mm ≤ D1 ≤ 5mm. This ensures the oil supply of the oil passage 32 while preventing leakage, increasing the cooling capacity of the rotary pump, and reducing frictional power consumption.

[0044] Optionally, the cross-section of the oil passage 32 can be circular, elliptical, or polygonal.

[0045] Preferably, the cross-section of the oil passage 32 is circular.

[0046] It should be noted that in this application, the number of oil passage holes 32 is one or more; wherein, when there are multiple oil passage holes 32, at least two of the multiple oil passage holes 32 are at different heights in the axial direction of the piston sleeve 30; or, the multiple oil passage holes 32 are at the same height in the axial direction of the piston sleeve 30.

[0047] It should be noted that in this application, there is a phase difference of a first included angle A between the two eccentric portions 12, the eccentricity of the two eccentric portions 12 is equal, and there is a limiting difference of a second included angle B between the extending directions of the two limiting channels 31, wherein the first included angle A is twice the second included angle B. Thus, by setting the piston sleeve 30 to a structure with two limiting channels 31 and correspondingly setting two pistons 40, the two eccentric portions 12 of the rotating shaft 10 extend into the two through holes 41 of the two pistons 40. Simultaneously, the two pistons 40 are slidably disposed within the two limiting channels 31, forming a variable volume cavity 311. Since the first included angle A between the two eccentric portions 12 is twice the second included angle B between the extending directions of the two limiting channels 31, when one of the two pistons 40 is at a dead position, that is, the driving of the eccentric portion 12 corresponding to the piston 40 at the dead position... When the torque is 0, the piston 40, which is at a dead position, cannot continue to rotate. At this time, the driving torque of the other eccentric part 12 driving the corresponding piston 40 is at its maximum value, ensuring that the eccentric part 12 with the maximum driving torque can normally drive the corresponding piston 40 to rotate. This piston 40 drives the piston sleeve 30 to rotate, and then the piston sleeve 30 drives the piston 40, which is at a dead position, to continue to rotate. This achieves stable operation of the fluid machinery, avoids the dead position of the motion mechanism, improves the motion reliability of the fluid machinery, and thus ensures the working reliability of the heat exchange equipment.

[0048] Optionally, there are two oil passage holes 32, and there is a limiting difference of a third included angle C between the extending directions of the two oil passage holes 32, and the third included angle C is equal to the second included angle B.

[0049] like Figure 1 As shown, the rotary cylinder pump also includes an upper flange 51 and a lower flange 52, which are respectively disposed at both ends of the cylinder liner 20.

[0050] The present invention provides a rotary cylinder pump, comprising a rotating shaft 10, a cylinder liner 20, a piston sleeve 30, and a piston 40. The rotating shaft 10 has a lubrication passage 11 extending axially along the rotating shaft 10 and penetrating one axial end of the rotating shaft 10, thereby communicating with an oil sump. The rotating shaft 10 also has two eccentric portions 12 along its axial direction. The rotating shaft 10 is eccentrically positioned to the cylinder liner 20 with a fixed eccentricity. The piston sleeve 30 is rotatably disposed within the cylinder liner 20 and has two limiting channels 31, both of which are sequentially arranged axially along the rotating shaft 10, with the extending direction of the limiting channels 31 perpendicular to the axial direction of the rotating shaft 10. The piston 40 has a through hole 41, and there are two pistons 40, with the two eccentric portions 12 correspondingly extending into them. The two pistons 40 are slidably disposed in the two through holes 41 of the two pistons 40 and in the two limiting channels 31 to form a variable volume cavity 311. The variable volume cavity 311 is located in the sliding direction of the pistons 40. The rotating shaft 10 rotates to drive the pistons 40 to slide back and forth in the limiting channels 31 and interact with the piston sleeve 30, so that the piston sleeve 30 and the pistons 40 rotate in the cylinder liner 20. The piston sleeve 30 has an oil passage 32 that passes through the inner and outer circumferential surfaces of the piston sleeve 30. The rotating shaft 10 also has a connecting hole 13 for connecting the lubricating oil passage 11 and the oil passage 32, so that the refrigeration oil in the oil sump flows into the space between the outer circumferential surface of the piston sleeve 30 and the inner circumferential surface of the cylinder liner 20 in sequence through the lubricating oil passage 11, the connecting hole 13, and the oil passage 32.

[0051] By providing a lubricating oil passage 11 and a connecting hole 13 on the rotating shaft 10, and an oil passage hole 32 on the piston sleeve 30, during the rotation of the rotating shaft 10, the refrigerant oil drawn into the lubricating oil passage 11 is transported sequentially through the connecting hole 13 and the oil passage hole 32 to the outer circumferential surface of the piston sleeve 30 and the inner circumferential surface of the cylinder liner 20 through centrifugal force. This lubricates the contact surfaces between the two, reduces the frictional power consumption between them, and helps to improve the energy efficiency of the rotary cylinder pump.

[0052] 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.

[0053] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this 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 drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0054] 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.

[0055] 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.

[0056] 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.

[0057] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A rotary cylinder pump, characterized in that, include: A rotating shaft (10) has a lubricating oil passage (11) which extends along the axial direction of the rotating shaft (10) and passes through one axial end of the rotating shaft (10) so that the lubricating oil passage (11) is connected to the oil sump. The rotating shaft (10) is also provided with two eccentric parts (12) 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 (30), the piston sleeve (30) is rotatably disposed in the cylinder sleeve (20), the piston sleeve (30) has two limiting channels (31), the two limiting channels (31) are arranged sequentially along the axial direction of the rotating shaft (10), and the extending direction of the limiting channels (31) is perpendicular to the axial direction of the rotating shaft (10); Piston (40), the piston (40) has a through hole (41), there are two pistons (40), the two eccentric parts (12) extend into the two through holes (41) of the two pistons (40), the two pistons (40) are slidably disposed in the two limiting channels (31) and form a variable volume cavity (311), the variable volume cavity (311) is located in the sliding direction of the piston (40), the rotating shaft (10) rotates to drive the piston (40) to slide back and forth in the limiting channel (31) while interacting with the piston sleeve (30) so that the piston sleeve (30) and the piston (40) rotate in the cylinder liner (20); The piston sleeve (30) has an oil passage hole (32) that passes through the inner and outer circumferential surfaces of the piston sleeve (30). The rotating shaft (10) also has a connecting hole (13) that connects the lubricating oil passage (11) and the oil passage hole (32) so that the refrigeration oil in the oil sump flows into the space between the outer circumferential surface of the piston sleeve (30) and the inner circumferential surface of the cylinder liner (20) through the lubricating oil passage (11), the connecting hole (13), and the oil passage hole (32) in sequence.

2. The rotary pump according to claim 1, characterized in that, The piston sleeve (30) has a central hole (33), the two limiting channels (31) are connected through the central hole (33), and the diameter of the central hole (33) is larger than the diameter of the shaft body portion of the rotating shaft (10); The oil passage (32) extends radially along the piston sleeve (30) and penetrates the hole wall of the central hole (33), and the connecting hole (13) extends radially along the shaft (10) and penetrates the shaft portion located in the central hole (33).

3. The rotary pump according to claim 1, characterized in that, The cylinder liner (20) has a liquid inlet channel (21), which extends radially and penetrates the outer peripheral surface of the cylinder liner (20). The inner wall surface of the cylinder liner (20) also has two liquid suction chambers (22), which are spaced apart along the axial direction of the cylinder liner (20). The cylinder liner (20) also has a through hole (24), which penetrates the two axial end faces of the cylinder liner (20) and is used to connect the two liquid suction chambers (22) with the liquid inlet channel (21) so that the refrigerant flows sequentially through the liquid inlet channel (21), the through hole (24), and the two liquid suction chambers (22) to the corresponding two variable volume chambers (311); The following conditions must be met: the diameter D1 of the oil passage hole (32), the first sealing height H1 of the oil passage hole (32) and the liquid suction chamber (22) on the axial direction of the cylinder liner (20), and the distance H2 between the first opening of the two liquid suction chambers (22) and the corresponding two variable volume chambers (311) on the axial direction of the cylinder liner (20) are: 0.1mm≤H1≤H2-D1-0.1mm.

4. The rotary pump according to claim 1, characterized in that, The cylinder liner (20) has two drain channels (23). The two drain channels (23) are spaced apart along the axial direction of the cylinder liner (20), and both drain channels (23) extend radially along the cylinder liner (20) and penetrate the outer circumferential surface of the cylinder liner (20). The two drain channels (23) are not connected. The following conditions must be met: the diameter D1 of the oil passage (32), the second sealing height H3 of the oil passage (32) and the drain channel (23) on the axial direction of the cylinder liner (20), and the distance H4 between the second openings of the two drain channels (23) and the corresponding two variable volume cavities (311) on the axial direction of the cylinder liner (20) are: 0.1mm≤H3≤H4-D1-0.1mm.

5. The rotary pump according to claim 1, characterized in that, The following conditions must be met: the diameter D1 of the oil passage (32), the third sealing height H5 of the oil passage (32) and the limiting channel (31) on the axial direction of the piston sleeve (30), and the axial spacing H6 of the two limiting channels (31) on the piston sleeve (30): 0.1mm≤H5≤H6-D1-0.1mm.

6. The rotary pump according to claim 1, characterized in that, The diameter D1 of the oil passage (32) satisfies: 0.5mm≤D1≤5mm.

7. The rotary pump according to claim 1, characterized in that, The cross-section of the oil passage (32) is one of the following: circular, elliptical, or polygonal.

8. The rotary pump according to claim 1, characterized in that, The number of the oil passage holes (32) is one or more; Wherein, when there are multiple oil passage holes (32), at least two of the multiple oil passage holes (32) are at different heights in the axial direction of the piston sleeve (30); or, The multiple oil passage holes (32) are all at the same height in the axial direction of the piston sleeve (30).

9. The rotary pump according to any one of claims 1 to 8, characterized in that, There is a phase difference of a first included angle A between the two eccentric portions (12), the eccentricity of the two eccentric portions (12) is equal, and there is a limiting difference of a second included angle B between the extending directions of the two limiting channels (31), wherein the first included angle A is twice the second included angle B.

10. The rotary pump according to claim 9, characterized in that, There are two oil passage holes (32), and there is a limiting difference of a third included angle C between the extending directions of the two oil passage holes (32), and the third included angle C is equal to the second included angle B.

11. A heat exchange device, characterized in that, Includes a rotary cylinder pump, wherein the rotary cylinder pump is the rotary cylinder pump according to any one of claims 1 to 10.

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