Pump body assembly and fluid machine

Abstract

The application provides a pump body assembly and a fluid machine. The pump body assembly comprises: a crankshaft; a cylinder sleeve, the crankshaft and the cylinder sleeve are eccentrically arranged and the eccentric distance is fixed; a piston assembly, the piston assembly has a variable volume chamber, the piston assembly is rotatably arranged in the cylinder sleeve, and the crankshaft is drivingly connected with the piston assembly to change the volume of the variable volume chamber; two flanges, the two flanges are arranged at the axial two ends of the cylinder sleeve respectively; the cylinder sleeve is provided with a liquid inlet channel and a first liquid outlet channel, at least one flange is provided with a second liquid outlet channel, the liquid inlet channel is communicated with the variable volume chamber and transports refrigerant into the variable volume chamber, and the first liquid outlet channel and the second liquid outlet channel are respectively communicated with the variable volume chamber and discharge the refrigerant in the variable volume chamber through the first liquid outlet channel and the second liquid outlet channel. The application solves the problem of poor operation reliability of the pump body assembly in the prior art.

Description

Technical Field

[0001] This invention relates to the field of heat exchange equipment technology, and more specifically, to a pump assembly and fluid machinery. 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 can meet 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. In this case, a liquid pump can be used instead of a compressor to drive the refrigerant in the system. This method is more energy efficient than conventional air conditioning systems. In the industry, this system that uses a pump to drive the refrigerant is called a refrigerant pump system; the pump that drives the refrigerant is called a refrigerant pump.

[0004] However, existing fluorine pumps suffer from uneven piston force due to the large pressure difference between the inlet and outlet sides of the cylinder liner and between the compression chamber and the inlet chamber in the pump body assembly. The high-pressure side always pushes the piston towards the low-pressure side, resulting in greater force on the bearing side of the inner circle of the cylinder liner. This leads to increased wear and frictional power consumption on the low-pressure bearing side of the inner circle of the cylinder liner, which greatly affects the performance and operational reliability of the fluorine pump.

[0005] As can be seen from the above, the existing technology has the problem of poor operational reliability of the pump body components. Summary of the Invention

[0006] The main objective of this invention is to provide a pump body assembly and fluid machinery to solve the problem of poor operational reliability of pump body assemblies in the prior art.

[0007] To achieve the above objectives, according to one aspect of the present invention, a pump body assembly is provided, comprising: a crankshaft; a cylinder liner, wherein the crankshaft and the cylinder liner are eccentrically disposed with a fixed eccentricity; a piston assembly having a variable volume chamber, the piston assembly being rotatably disposed within the cylinder liner, and the crankshaft being drivenly connected to the piston assembly to change the volume of the variable volume chamber; two flanges, the two flanges being respectively disposed at both axial ends of the cylinder liner; the cylinder liner being provided with an inlet channel and a first drain channel, and at least one flange being provided with a second drain channel, the inlet channel communicating with the variable volume chamber and supplying refrigerant into the variable volume chamber, the first drain channel and the second drain channel respectively communicating with the variable volume chamber and discharging the refrigerant in the variable volume chamber through the first drain channel and the second drain channel.

[0008] Furthermore, the first drain channel penetrates the inner and outer walls of the cylinder liner radially, and the second drain channel at least partially overlaps with the variable volume cavity in the axial direction.

[0009] Furthermore, the radial cross-sectional area S1 of the variable volume cavity and the effective area S2 of the first drainage channel satisfy: 1≤S1 / S2≤2.

[0010] Furthermore, the radial cross-sectional area S1 of the variable volume cavity and the effective area S3 of the second drainage channel satisfy: 2≤S1 / S3<3.

[0011] Furthermore, when the piston assembly operates at an angle of 0°, there is a sealing angle α between the piston assembly and the cylinder liner.

[0012] Furthermore, the sealing angle α satisfies: 0≤α≤10°.

[0013] Furthermore, when the piston assembly operates at an angle of θ1, the variable volume chamber is connected to the second drainage channel; when the piston assembly operates at an angle of 180°-θ2, the variable volume chamber is disconnected from the second drainage channel, wherein α≤θ1≤90° and α≤θ2≤90°.

[0014] Furthermore, the second drainage channel can be in the shape of a straight line, an L-shape, an arc shape, or a round hole.

[0015] Furthermore, the piston assembly includes: a piston sleeve rotatably disposed within a cylinder liner, the piston sleeve having a limiting channel extending perpendicular to the axial direction of the crankshaft; and a piston slidably disposed within the limiting channel to form a variable volume cavity, the variable volume cavity being located in the sliding direction of the piston, the piston having a sliding groove, the piston sliding relative to the crankshaft during crankshaft rotation to allow the crankshaft to slide into contact with the groove wall surface of the sliding groove, and the piston rotating with the crankshaft under the drive of the crankshaft while simultaneously reciprocating within the piston sleeve along an axial direction perpendicular to the crankshaft.

[0016] Furthermore, the crankshaft is provided with two eccentric portions along its axial direction. The piston assembly includes: a piston sleeve, which is rotatably disposed within the cylinder liner and has two limiting channels arranged sequentially along the axial direction of the crankshaft, with the extension direction of the limiting channels perpendicular to the axial direction of the crankshaft; and two pistons, each with a through hole. 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 and form two variable volume cavities respectively. The two variable volume cavities are located in the sliding direction of the two pistons respectively. The crankshaft rotates to drive the pistons to reciprocate within the limiting channels while interacting with the piston sleeve, so that the piston sleeve and the pistons rotate within the cylinder liner.

[0017] Furthermore, the two eccentric parts are arranged at a 180° angle.

[0018] Furthermore, the limiting channel has a set of opposing first sliding surfaces that slide in contact with the piston, the piston has a second sliding surface that cooperates with the first sliding surface, the piston has a pressing surface facing the end of the limiting channel, the pressing surface serves as the head of the piston, the two second sliding surfaces are connected through the pressing surface, and the pressing surface faces the variable volume cavity.

[0019] Furthermore, there are two first drainage channels, and two flanges are respectively provided with second drainage channels. The two variable volume cavities are respectively connected to one first drainage channel and one second drainage channel.

[0020] Furthermore, the cylinder liner is also equipped with an inlet buffer tank, and the inlet channel is connected to both variable volume chambers through the inlet buffer tank.

[0021] Furthermore, the inlet channel and the first outlet channel are arranged 180° opposite each other in the circumferential direction of the pump body assembly, and the first outlet channel and the second outlet channel are correspondingly arranged along the axial direction of the pump body assembly.

[0022] According to another aspect of the invention, a fluid machine is provided, comprising the pump body assembly described above.

[0023] Furthermore, the fluid machinery is a fluorine pump.

[0024] The pump assembly using the technical solution of this invention includes a crankshaft, a cylinder liner, a piston assembly, and flanges. The crankshaft and cylinder liner are eccentrically arranged with a fixed eccentricity. The piston assembly has a variable volume chamber and is rotatably disposed within the cylinder liner. The crankshaft and piston assembly are drivenly connected to change the volume of the variable volume chamber. There are two flanges, respectively disposed at both axial ends of the cylinder liner. The cylinder liner is provided with an inlet channel and a first outlet channel. At least one flange is provided with a second outlet channel. The inlet channel communicates with the variable volume chamber and supplies refrigerant into it. The first outlet channel and the second outlet channel are respectively connected to the variable volume chamber and discharge the refrigerant from the variable volume chamber through the first outlet channel and the second outlet channel. Thus, by means of the flanges... Adding a second drainage channel reduces the area of ​​the first drainage channel on the cylinder liner while ensuring drainage, thereby reducing the area of ​​the piston assembly subjected to high-pressure thrust. This reduces wear and frictional power consumption on the low-pressure bearing side of the cylinder liner's inner circle. Furthermore, it reduces drainage resistance, alleviates instantaneous pressure during drainage, reduces over-compression, mitigates insufficient drainage of the pump assembly, and improves efficiency. In addition, the second drainage channel increases pressure on the piston end face of the piston assembly, thereby reducing piston tilt during pump assembly operation, reducing wear between the piston end face and the flange end face, improving lubrication, and significantly improving the operational reliability of the pump assembly. This solves the problem of poor operational reliability of pump assemblies in existing technologies. Attached Figure Description

[0025] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0026] Figure 1 An exploded view of a pump body assembly according to a specific embodiment of the present invention is shown;

[0027] Figure 2 A cross-sectional view of a pump body assembly according to a specific embodiment of the present invention is shown;

[0028] Figure 3 A schematic diagram of the sealing angle of the pump body assembly in a specific embodiment of the present invention is shown;

[0029] Figure 4 This diagram illustrates the flange starting to drain fluid in a specific embodiment of the present invention.

[0030] Figure 5 This diagram illustrates the flange at the end of the draining process in a specific embodiment of the present invention.

[0031] Figure 6 A schematic diagram of the radial cross-sectional area S1 of the variable volume cavity in a specific embodiment of the present invention is shown;

[0032] Figure 7 A schematic diagram of the effective area S2 of the first drainage channel in a specific embodiment of the present invention is shown;

[0033] Figure 8 A schematic diagram of the effective area S3 of the second drainage channel in a specific embodiment of the present invention is shown.

[0034] The above figures include the following reference numerals:

[0035] 10. Crankshaft; 11. Eccentric part; 20. Cylinder liner; 21. Liquid inlet channel; 22. First drain channel; 23. Liquid inlet buffer tank; 24. Liquid inlet chamber; 30. Piston assembly; 31. Piston sleeve; 311. Limiting channel; 312. Variable volume chamber; 32. Piston; 321. Through hole; 322. Extrusion surface; 323. Pressure relief guide groove; 40. Flange; 41. Second drain channel. Detailed Implementation

[0036] 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.

[0037] To address the problem of poor operational reliability of pump assemblies in existing technologies, this invention provides a pump assembly and a fluid machine. The fluid machine includes the pump assembly described below.

[0038] like Figures 1 to 8 As shown, the pump assembly includes a crankshaft 10, a cylinder liner 20, a piston assembly 30, and a flange 40. The crankshaft 10 is eccentrically positioned relative to the cylinder liner 20 with a fixed eccentricity. The piston assembly 30 has a variable volume chamber 312 and is rotatably mounted within the cylinder liner 20. The crankshaft 10 is driven to the piston assembly 30 to change the volume of the variable volume chamber 312. There are two flanges 40, which are respectively located at both axial ends of the cylinder liner 20. The cylinder liner 20 is provided with an inlet channel 21 and a first drain channel 22, and at least one flange 40 is provided with a second drain channel 41. The inlet channel 21 communicates with the variable volume chamber 312 and supplies refrigerant into it. The first drain channel 22 and the second drain channel 41 are respectively connected to the variable volume chamber 312 and discharge the refrigerant from the variable volume chamber 312 through the first drain channel 22 and the second drain channel 41.

[0039] By adding a second drain channel 41 to the flange 40, the area of ​​the first drain channel 22 on the cylinder liner 20 can be reduced while ensuring drainage. This reduces the area of ​​the piston assembly 30 subjected to high-pressure side thrust, thereby reducing wear and frictional power consumption on the low-pressure bearing side of the inner circle of the cylinder liner 20. Furthermore, it can reduce drainage resistance, alleviate instantaneous pressure during drainage, reduce over-compression, mitigate insufficient drainage of the pump body assembly, and improve efficiency. In addition, the second drain channel 41 can also increase pressure on the piston end face of the piston assembly 30, thereby reducing piston tilt during pump body assembly operation, reducing wear between the piston end face and the flange end face, improving lubrication, and greatly improving the operational reliability of the pump body assembly.

[0040] In this embodiment, the inlet channel 21 and the first outlet channel 22 are arranged 180° opposite each other in the circumferential direction of the pump body assembly, that is, the inlet channel 21 and the first outlet channel 22 are arranged opposite each other on the cylinder liner 20. The first outlet channel 22 and the second outlet channel 41 are arranged correspondingly along the axial direction of the pump body assembly, that is, the first outlet channel 22 and the second outlet channel 41 are arranged vertically correspondingly and located on the same side. Furthermore, the second outlet channel 41 and the variable volume cavity 312 at least partially overlap in the axial direction of the pump body assembly, thereby enabling communication with the variable volume cavity 312.

[0041] In this embodiment, the first drain channel 22 radially penetrates the inner and outer walls of the cylinder liner 20. That is, on the drain side, the cylinder liner does not have any other channels or grooves. Correspondingly, on the inlet side, the cylinder liner 20 is also provided with an inlet buffer groove 23, and the inlet channel 21 communicates with the variable volume cavity 312 through the inlet buffer groove 23. Specifically, the inlet buffer groove 23 extends a predetermined distance circumferentially along the cylinder liner 20 to form an arc-shaped inlet buffer groove 23, and the diameter of the inlet channel 21 and / or the diameter of the first drain channel 22 is smaller than the arc length of the arc-shaped inlet buffer groove 23. This ensures that the inlet buffer groove 23 can effectively buffer the refrigerant, thereby helping to reduce inlet pressure pulsation in the pump assembly.

[0042] Furthermore, such as Figures 3 to 5 As shown, the inner wall of the cylinder liner 20 has a liquid inlet chamber 24, which is connected to the liquid inlet channel 21. The liquid inlet chamber 24 extends circumferentially along the inner wall of the cylinder liner 20 by a predetermined distance to form an arc-shaped liquid inlet chamber 24. The arc length of the arc-shaped liquid inlet buffer groove 23 is not less than the arc length of the arc-shaped liquid inlet chamber 24. This ensures that the liquid inlet buffer groove 23 can effectively buffer the refrigerant, thereby helping to reduce the inlet pressure pulsation of the pump body assembly.

[0043] In this embodiment, the line connecting the center of the arc length of the arc-shaped liquid inlet buffer tank 23 and the center of the arc length of the arc-shaped liquid inlet cavity 24 passes through the geometric center of the cylinder liner 20. This ensures the reliability of the liquid inlet buffer tank 23 in buffering the refrigerant.

[0044] like Figures 1 to 6As shown, the piston assembly 30 includes a piston sleeve 31 and a piston 32. The piston sleeve 31 is rotatably disposed within the cylinder liner 20 and has a limiting channel 311 extending perpendicularly to the axial direction of the crankshaft 10. The piston 32 is slidably disposed within the limiting channel 311 to form a variable volume cavity 312, which is located in the sliding direction of the piston 32. The piston 32 has a sliding groove. During the rotation of the crankshaft 10, the piston 32 slides relative to the crankshaft 10, so that the crankshaft 10 slides into contact with the groove wall of the sliding groove. Under the drive of the crankshaft 10, the piston 32 rotates with the crankshaft 10 and simultaneously slides reciprocally within the piston sleeve 31 along an axial direction perpendicular to the crankshaft 10.

[0045] In this embodiment, as Figure 1 As shown, the crankshaft 10 has two eccentric portions 11 along its axial direction. Correspondingly, the piston 32 has a through hole 321. There are two pistons 32. The two eccentric portions 11 extend into the two through holes 321 of the two pistons 32. The two pistons 32 are slidably disposed in the two limiting channels 311 and form two variable volume cavities 312 respectively. The two variable volume cavities 312 are respectively located in the sliding direction of the two pistons 32. The crankshaft 10 rotates to drive the pistons 32 to slide back and forth in the limiting channels 311 while interacting with the piston sleeve 31, so that the piston sleeve 31 and the pistons 32 rotate in the cylinder liner 20.

[0046] Preferably, the two eccentric portions 11 are arranged at a 180° angle.

[0047] In this embodiment, the two eccentric portions 11 have a phase difference of a first included angle, the eccentricity of the two eccentric portions 11 is equal, and the extension directions of the two limiting channels 311 have a limiting difference of a second included angle, wherein the first included angle is twice the second included angle. Thus, when one of the two pistons 32 is at a dead position, that is, the driving torque of the eccentric portion 11 corresponding to the piston 32 at the dead position is 0, the piston 32 at the dead position cannot continue to rotate. At this time, the driving torque of the other eccentric portion 11 driving the corresponding piston 32 is at its maximum value, ensuring that the eccentric portion 11 with the maximum driving torque can normally drive the corresponding piston 32 to rotate, thereby driving the piston sleeve 31 to rotate through the piston 32, and then driving the piston 32 at the dead position to continue rotating through the piston sleeve 31, thus achieving stable operation of the rotary pump.

[0048] like Figure 1As shown, the limiting channel 311 has a set of opposing first sliding surfaces that slide in contact with the piston 32. The piston 32 has a second sliding surface that cooperates with the first sliding surfaces. The piston 32 has a pressing surface 322 facing the end of the limiting channel 311, which serves as the head of the piston 32. The two second sliding surfaces are connected by the pressing surface 322, which faces the variable volume cavity 312. Furthermore, a pressure relief guide groove 323 is also provided on the pressing surface 322.

[0049] In this embodiment, when the pump assembly is running, the crankshaft 10 rotates around its axis; the piston sleeve 31 revolves around the axis of the crankshaft 10, with the axis of the crankshaft 10 and the axis of the piston sleeve 31 eccentrically positioned with a fixed eccentricity; the first piston 32 performs circular motion around the axis of the crankshaft 10, and the distance between the center of the first piston 32 and the axis of the crankshaft 10 is equal to the eccentricity of the first eccentric portion 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentricity distance between the axis of the crankshaft 10 and the axis of the piston sleeve 31. The crankshaft 10 rotates to drive the first piston 32 to perform circular motion, and The first piston 32 interacts with the piston sleeve 31 and slides back and forth within the limiting channel 311 of the piston sleeve 31; the second piston 32 makes a circular motion with the axis of the crankshaft 10 as the center, and the distance between the center of the second piston 32 and the axis of the crankshaft 10 is equal to the eccentricity of the second eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentric distance between the axis of the crankshaft 10 and the axis of the piston sleeve 31. The crankshaft 10 rotates to drive the second piston 32 to make a circular motion, and the second piston 32 interacts with the piston sleeve 31 and slides back and forth within the limiting channel 311 of the piston sleeve 31.

[0050] The pump assembly in this embodiment constitutes a cross-slider mechanism, and the operating method adopts the principle of the cross-slider mechanism.

[0051] In this embodiment, the running trajectory of the piston 32 is a circle, with the center of the crankshaft 10 and the radius of the line connecting the center of the crankshaft 10 and the center of the piston sleeve 31.

[0052] In this embodiment, the inlet channel 21 is connected to both variable volume chambers 312 via the inlet buffer tank 23. There are two first drain channels 22, and each of the two flanges 40 (upper and lower flanges) is provided with a second drain channel 41. Each of the two variable volume chambers 312 is connected to one first drain channel 22 and one second drain channel 41. In other words, the variable volume chambers 312 correspond one-to-one with the first drain channel 22 and the second drain channel 41. By providing second drain channels 41 on the upper and lower flanges, pressure can be increased on the upper and lower end faces of the piston assembly 30, thereby reducing piston tilt during pump assembly operation, reducing wear on the piston end face and flange end face, improving lubrication, and greatly improving the operational reliability of the pump assembly.

[0053] In this embodiment, as Figures 6 to 8 As shown, during operation, a single variable volume chamber 312 of the pump assembly consists of a piston groove surface, a piston head surface, a flange end face, and an inner circular surface of the cylinder liner. The radial cross-sectional area of ​​the variable volume chamber 312 is S1. The radial cross-sectional area S1 of the variable volume chamber 312 and the effective area S2 of the first drainage channel 22 satisfy: 1 ​​≤ S1 / S2 ≤ 2. The radial cross-sectional area S1 of the variable volume chamber 312 and the effective area S3 of the second drainage channel 41 satisfy: 2 ≤ S1 / S3 < 3. Through the above settings, it can be ensured that the combined drainage channel area of ​​the first drainage channel 22 and the second drainage channel 41 meets the requirements that there is no drainage loss or drainage resistance during the operation of the pump assembly, thereby reducing power consumption and improving performance.

[0054] It is understandable that the effective area of ​​the first drainage channel 22 is the radial cross-sectional area of ​​the first drainage channel 22, and the effective area of ​​the second drainage channel 41 is the area of ​​the part of the second drainage channel 41 that overlaps with the variable volume cavity 312.

[0055] like Figure 3 As shown, when the piston assembly 30 operates at 0°, there is a sealing angle α between the piston assembly 30 and the cylinder liner 20. At this time, the inlet chamber 24, the variable volume chamber 312, and the discharge channel are separated. Furthermore, when the piston assembly 30 operates from α to 180°-α, one variable volume chamber 312 of the piston assembly 30 completes the low-pressure refrigerant suction process, and the other variable volume chamber 312 completes the high-pressure refrigerant discharge process. The sealing angle α satisfies: 0 ≤ α ≤ 10°. Through the above settings, the operational reliability of the pump body assembly can be guaranteed while ensuring the sealing reliability of the pump body assembly.

[0056] like Figures 4 to 5 As shown, when the operating angle of the piston assembly 30 is θ1, the variable volume chamber 312 is connected to the second drainage channel 41. When the operating angle of the piston assembly 30 is 180°-θ2, the variable volume chamber 312 is disconnected from the second drainage channel 41. During this drainage process, the first drainage channel 22 and the second drainage channel 41 jointly complete the drainage process. Wherein, α≤θ1≤90°, α≤θ2≤90°. Through the above settings, a certain sealing distance can be ensured between the variable volume chamber 312 and the drainage port, preventing leakage loss in the pump assembly during operation and ensuring no impact on performance.

[0057] In this embodiment, the second drainage channel 41 is in the shape of a straight line, an L-shape, an arc, or a circular hole. Of course, the second drainage channel 41 can also be other shapes, and the specific shape is determined according to the actual drainage volume requirements and process requirements.

[0058] This application also provides a fluid machine, including the pump body assembly described above. Specifically, the pump body assembly is a fluorine pump.

[0059] As can be seen from the above description, the above embodiments of the present invention achieve the following technical effects: by adding a second drain channel 41 to the flange 40, the area of ​​the first drain channel 22 on the cylinder liner 20 can be reduced while ensuring draining, thereby reducing the area of ​​the piston assembly 30 subjected to high-pressure side thrust, and further reducing the wear and friction power consumption on the low-pressure bearing side of the inner circle of the cylinder liner 20. In addition, it can also reduce the draining resistance, reduce the instantaneous pressure during the draining process, reduce over-compression, reduce the situation of insufficient draining of the pump body assembly, and improve efficiency. Furthermore, the second drain channel 41 can also increase the pressure on the piston end face of the piston assembly 30, thereby reducing the tilting of the piston when the pump body assembly is in operation, reducing the wear between the piston end face and the flange end face, improving lubrication, and greatly improving the operational reliability of the pump body assembly.

[0060] 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.

[0061] 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.

[0062] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0063] 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.

[0064] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0065] 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.

[0066] 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.

[0067] The above are merely preferred embodiments of the present invention and are not intended to limit the present 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, characterized in that, include: Crankshaft (10); Cylinder liner (20), the crankshaft (10) and the cylinder liner (20) are eccentrically arranged and the eccentric distance is fixed; A piston assembly (30) having a variable volume chamber (312) is rotatably disposed within the cylinder liner (20), and the crankshaft (10) is drivenly connected to the piston assembly (30) to change the volume of the variable volume chamber (312). Flange (40), there are two flanges (40), and the two flanges (40) are respectively disposed at both ends of the cylinder liner (20); The cylinder liner (20) is provided with a liquid inlet channel (21) and a first liquid outlet channel (22), and at least one of the flanges (40) is provided with a second liquid outlet channel (41). The liquid inlet channel (21) is connected to the variable volume chamber (312) and supplies refrigerant into the variable volume chamber (312). The first liquid outlet channel (22) and the second liquid outlet channel (41) are respectively connected to the variable volume chamber (312) and discharge the refrigerant in the variable volume chamber (312) through the first liquid outlet channel (22) and the second liquid outlet channel (41). The radial cross-sectional area S1 of the variable volume cavity (312) and the effective area S3 of the second drainage channel (41) satisfy: 2≤S1 / S3<3.

2. The pump body assembly according to claim 1, characterized in that, The first drain channel (22) penetrates the inner and outer walls of the cylinder liner (20) radially, and the second drain channel (41) and the variable volume cavity (312) at least partially overlap in the axial direction.

3. The pump body assembly according to claim 1, characterized in that, The radial cross-sectional area S1 of the variable volume cavity (312) and the effective area S2 of the first drainage channel (22) satisfy: 1≤S1 / S2≤2.

4. The pump body assembly according to claim 1, characterized in that, When the operating angle of the piston assembly (30) is 0°, there is a sealing angle α between the piston assembly (30) and the cylinder liner (20).

5. The pump body assembly according to claim 4, characterized in that, The sealing angle α satisfies: 0≤α≤10°.

6. The pump body assembly according to claim 5, characterized in that, When the operating angle of the piston assembly (30) is θ1, the variable volume cavity (312) is connected to the second drainage channel (41). When the operating angle of the piston assembly (30) is 180°-θ2, the variable volume cavity (312) is disconnected from the second drainage channel (41), wherein α≤θ1≤90° and α≤θ2≤90°.

7. The pump body assembly according to claim 1, characterized in that, The second drainage channel (41) is in the shape of a straight line, an L-shape, an arc shape, or a round hole.

8. The pump body assembly according to claim 1, characterized in that, The piston assembly (30) includes: Piston sleeve (31), the piston sleeve (31) is rotatably disposed within the cylinder sleeve (20), the piston sleeve (31) has a limiting channel (311), the extending direction of the limiting channel (311) is perpendicular to the axial direction of the crankshaft (10); The piston (32) is slidably disposed in the limiting channel (311) to form the variable volume cavity (312), and the variable volume cavity (312) is located in the sliding direction of the piston (32). The piston (32) has a sliding groove. During the rotation of the crankshaft (10), the piston (32) slides relative to the crankshaft (10) so that the crankshaft (10) slides in cooperation with the groove wall surface of the sliding groove. The piston (32) rotates with the crankshaft (10) under the drive of the crankshaft (10) and simultaneously slides back and forth in the piston sleeve (31) along an axial direction perpendicular to the crankshaft (10).

9. The pump body assembly according to claim 1, characterized in that, The crankshaft (10) is provided with two eccentric portions (11) along its axial direction, and the piston assembly (30) includes: 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 crankshaft (10), and the extending direction of the limiting channels (311) is perpendicular to the axial direction of the crankshaft (10); Piston (32), the piston (32) has a through hole (321), there are two pistons (32), the two eccentric parts (11) extend into the two through holes (321) of the two pistons (32), the two pistons (32) are slidably disposed in the two limiting channels (311) and respectively form two variable volume cavities (312), the two variable volume cavities (312) are respectively located in the sliding direction of the two pistons (32), the crankshaft (10) rotates to drive the piston (32) 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 (32) rotate in the cylinder liner (20).

10. The pump body assembly according to claim 9, characterized in that, The two eccentric parts (11) are arranged at a 180° angle.

11. The pump body assembly according to claim 8 or 9, characterized in that, The limiting channel (311) has a set of opposing first sliding surfaces that slide in contact with the piston (32). The piston (32) has a second sliding surface that cooperates with the first sliding surface. The piston (32) has a pressing surface (322) facing the end of the limiting channel (311). The pressing surface (322) serves as the head of the piston (32). The two second sliding surfaces are connected through the pressing surface (322). The pressing surface (322) faces the variable volume cavity (312).

12. The pump body assembly according to claim 9, characterized in that, There are two first drainage channels (22), and the two flanges (40) are respectively provided with second drainage channels (41). The two variable volume cavities (312) are respectively connected to one of the first drainage channels (22) and one of the second drainage channels (41).

13. The pump body assembly according to claim 9, characterized in that, The cylinder liner (20) is also provided with a liquid inlet buffer groove (23), and the liquid inlet channel (21) is connected to both of the variable volume chambers (312) through the liquid inlet buffer groove (23).

14. The pump body assembly according to claim 1, characterized in that, The inlet channel (21) and the first outlet channel (22) are arranged in a 180° opposite orientation in the circumferential direction of the pump body assembly, and the first outlet channel (22) and the second outlet channel (41) are arranged correspondingly along the axial direction of the pump body assembly.

15. A fluid machine, characterized in that, Includes the pump body assembly according to any one of claims 1 to 14.

16. The fluid machinery according to claim 15, characterized in that, The fluid machinery is a fluorine pump.

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