CN118088436A

CN118088436A - Rotary cylinder pump and heat exchange equipment

Info

Publication number: CN118088436A
Application number: CN202211491596.0A
Authority: CN
Inventors: 杜忠诚; 张培林; 任丽萍; 胡烜; 于瑞波; 丁宁
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2022-11-25
Filing date: 2022-11-25
Publication date: 2024-05-28

Abstract

The invention provides a rotary cylinder pump and heat exchange equipment, wherein the rotary cylinder pump comprises a pump body component, the pump body component comprises a rotating shaft, a cylinder sleeve and a piston component, and the cylinder sleeve are eccentrically arranged and have fixed eccentric distances; the piston assembly is provided with a variable-volume cavity, the piston assembly is rotatably arranged in the cylinder sleeve, and the rotating shaft is in driving connection with the piston assembly to change the volume of the variable-volume cavity; the inner wall surface of the cylinder sleeve is provided with a liquid suction cavity, and the liquid suction cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve for a first preset distance to form an arc-shaped liquid suction cavity; the inner wall surface of the cylinder sleeve is provided with a liquid draining cavity, the liquid draining cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve for a second preset distance to form an arc-shaped liquid draining cavity, and a sealing angle is formed between at least one side of the liquid draining cavity and/or at least one side of the liquid draining cavity and the outer wall surface of the piston assembly. The invention solves the problems of poor energy efficiency, poor stability and poor reliability of the heat exchange system in the prior art.

Description

Rotary cylinder pump and heat exchange equipment

Technical Field

The invention relates to the technical field of heat exchange systems, in particular to a rotary cylinder pump and heat exchange equipment.

Background

Along with the development of society, the power consumption of a data center is increased year by year, so that the power consumption is huge, and the air conditioner of a machine room is an important component of the data center and accounts for 40% of the power consumption of the data center, so that the application significance of the energy-saving technology is great.

A room air conditioner is a device for cooling electrical components of a data center, and needs to perform cooling uninterruptedly throughout the year to ensure that the indoor temperature can be maintained within a certain range. Most of the existing machine room air conditioners adopt a compression refrigeration technology, and the existing machine room air conditioners depend on a compression refrigeration system for cooling in summer or winter. When the ambient temperature is higher, the existing compression refrigeration technology can meet the performance and energy efficiency requirements; and when the outdoor environment temperature is obviously lower than the indoor temperature, the most economical and energy-saving refrigeration mode is to use the outdoor low temperature as the indoor temperature reduction. The industry has been exploring a low-temperature refrigeration mode which can fully utilize outdoor low temperature and has high economy, and in recent years, a fluorine pump-compression dual-circulation system is proposed, namely, in a high-temperature season, the existing compression refrigeration mode is adopted; in low temperature season, the low power fluorine pump is used to replace the high power compressor as power source to complete the refrigerating cycle, so as to realize energy saving effect.

However, the current fluorine pump-compression dual-circulation system of the machine room air conditioner mainly uses a centrifugal pump, and has the following problems: the centrifugal pump has relatively low hydraulic efficiency and seriously affects the energy efficiency of the refrigeration system; the flow and the lift of the centrifugal pump are mutually limited, namely, the lift is reduced when the flow is increased, which is contrary to the actual requirement of the refrigeration system; the centrifugal pump has a small lift range, and is influenced by uncertain factors such as pipe length, drop and the like during engineering installation, so that the required lift exceeds the design lift of the centrifugal pump, and the refrigerating capacity of a refrigerating system is seriously influenced. In addition, as the working medium of the fluorine pump-compression dual-circulation system is a liquid refrigerant, vaporization is easy to occur, and the centrifugal pump has no self-absorption capability, if the inlet is provided with air in the use process, idling can occur, and the operation reliability of the refrigeration system is seriously affected.

Disclosure of Invention

The invention mainly aims to provide a rotary cylinder pump and heat exchange equipment so as to solve the problems of poor energy efficiency, poor stability and poor reliability of a heat exchange system in the prior art.

In order to achieve the above object, according to one aspect of the present invention, there is provided a rotary cylinder pump including a pump body assembly including a rotary shaft, a cylinder liner and a piston assembly, the cylinder liner being eccentrically disposed from the cylinder liner with a fixed eccentric distance; the piston assembly is provided with a variable-volume cavity, the piston assembly is rotatably arranged in the cylinder sleeve, and the rotating shaft is in driving connection with the piston assembly to change the volume of the variable-volume cavity; the inner wall surface of the cylinder sleeve is provided with a liquid suction cavity, and the liquid suction cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve for a first preset distance to form an arc-shaped liquid suction cavity; the inner wall surface of the cylinder sleeve is provided with a liquid draining cavity, the liquid draining cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve for a second preset distance to form an arc-shaped liquid draining cavity, and a sealing angle is formed between at least one side of the liquid draining cavity and/or at least one side of the liquid draining cavity and the outer wall surface of the piston assembly.

Further, the sealing angle comprises a first sealing angle theta 4 and a second sealing angle theta 1, the first sealing angle theta 4 and the second sealing angle theta 1 are respectively arranged on two sides of the circumference of the liquid suction cavity, the first sealing angle theta 4 is the sealing angle at the beginning of suction, and the second sealing angle theta 1 is the sealing angle at the end of suction.

Further, the first sealing angle θ4 satisfies: theta 4 is more than or equal to 0 and less than or equal to 10 degrees; and/or, the second sealing angle θ1 satisfies: θ1 is more than or equal to 0 and less than or equal to 10 degrees.

Further, the first sealing angle θ4 satisfies: theta 4 is more than or equal to 1 degree and less than or equal to 5 degrees; and/or, the second sealing angle θ1 satisfies: theta 1 is more than or equal to 1 degree and less than or equal to 5 degrees.

Further, the sealing angles comprise a third sealing angle theta 3 and a fourth sealing angle theta 2, the third sealing angle theta 3 and the fourth sealing angle theta 2 are respectively arranged on two sides of the liquid draining cavity in the circumferential direction, wherein the third sealing angle theta 3 is the sealing angle at the end of the discharging, and the fourth sealing angle theta 2 is the sealing angle at the beginning of the discharging.

Further, the third sealing angle θ3 satisfies: theta 3 is more than or equal to 0 and less than or equal to 10 degrees; and/or, the fourth sealing angle θ2 satisfies: θ2 is more than or equal to 0 and less than or equal to 10 degrees.

Further, the third sealing angle θ3 satisfies: theta 3 is more than or equal to 1 degree and less than or equal to 5 degrees; and/or, the fourth sealing angle θ2 satisfies: theta 2 is more than or equal to 1 degree and less than or equal to 5 degrees.

Further, the piston assembly is provided with a piston sleeve, the piston sleeve is rotatably arranged in the cylinder sleeve, the sealing angles comprise a first sealing angle theta 4, a second sealing angle theta 1, a third sealing angle theta 3 and a fourth sealing angle theta 2, wherein the first sealing angle theta 4 is formed on the suction starting side of the piston assembly and the liquid suction cavity, the second sealing angle theta 1 is formed on the suction ending side of the piston assembly and the liquid suction cavity, the third sealing angle theta 2 is formed on the discharge starting side of the piston assembly and the liquid discharge cavity, and the fourth sealing angle theta 3 is formed on the discharge ending side of the piston assembly and the liquid discharge cavity; and the first sealing angle theta 4, the second sealing angle theta 1 are determined by the positions of the two ends of the piston sleeve and the arc-shaped liquid suction cavity, and the third sealing angle theta 2 and the fourth sealing angle theta 3 are determined by the positions of the two ends of the piston sleeve and the arc-shaped liquid suction cavity.

Further, theta 2-theta 1 is more than or equal to 0 degree and less than or equal to 5 degrees; and/or, 0 DEG is less than or equal to theta 3-theta 4 is less than or equal to 5 deg.

Further, the piston assembly is provided with a piston sleeve, the piston sleeve is rotatably arranged in the cylinder sleeve, the pump body assembly is provided with a liquid suction state and a liquid discharge state according to the rotation position change of the piston sleeve, the piston sleeve is provided with a suction starting position, a suction ending position, a discharge starting position and a discharge ending position, and when the piston sleeve is positioned at the suction starting position, the variable volume cavity is communicated with the liquid suction cavity; when the piston sleeve is positioned at the suction end position, the variable volume cavity is communicated with the liquid suction cavity; when the piston sleeve is positioned at the discharge starting position, the variable-volume cavity is communicated with the liquid discharge cavity; when the piston sleeve is at the discharge end position, the variable volume cavity is communicated with the liquid discharge cavity.

Further, the cylinder sleeve is provided with a liquid inlet channel and a liquid outlet channel, the liquid inlet channel and the liquid outlet channel are oppositely arranged at 180 degrees, the liquid inlet channel is communicated with the liquid suction cavity, and the liquid outlet channel is communicated with the liquid outlet cavity.

Further, the piston assembly comprises a piston sleeve and a piston, wherein the piston sleeve is rotatably arranged in the cylinder sleeve, the piston sleeve is provided with a limiting channel, and the extending direction of the limiting channel is perpendicular to the axial direction of the rotating shaft; the piston slides and sets up in order to form the volume-variable chamber in spacing passageway, and the volume-variable chamber is located the slip direction of piston, and the piston has the groove of sliding, and pivot pivoted in-process, the piston slides for the pivot to make pivot and the cell wall face sliding fit in the groove of sliding, and the piston rotates and simultaneously along the axial reciprocating sliding in the piston sleeve of perpendicular to pivot along the pivot under the drive of pivot.

Further, the rotating shaft is provided with two eccentric parts along the axial direction of the rotating shaft, the piston assembly comprises a piston sleeve and a piston, the piston sleeve is rotatably arranged in the cylinder sleeve, the piston sleeve is provided with two limiting channels, the two limiting channels are sequentially arranged along the axial direction of the rotating shaft, and the extending direction of the limiting channels is perpendicular to the axial direction of the rotating shaft; the piston has the through-hole, and the piston is two, and two eccentric parts correspond and stretch into in two through-holes of two pistons, and two pistons correspond the slip setting and become the volume chamber in two spacing passageway, and the pivot rotates in order to drive the piston and to interact with the piston sleeve in spacing passageway reciprocating sliding to make piston sleeve, piston rotate in the cylinder liner.

Further, a phase difference of a first included angle A is formed between the two eccentric parts, the eccentric amounts of the two eccentric parts are equal, and a limit difference of a second included angle B is formed between the extending directions of the two limit channels, wherein the first included angle A is twice the second included angle B.

Further, the two eccentric portions are arranged at an angle of 180 degrees.

Further, the limiting channel is provided with a set of oppositely arranged first sliding surfaces in sliding contact with the piston, the piston is provided with a second sliding surface matched with the first sliding surface, the piston is provided with an extrusion surface facing the end part of the limiting channel, the extrusion surface is used as the head part of the piston, the two second sliding surfaces are connected through the extrusion surface, and the extrusion surface faces the variable-volume cavity.

Further, the extrusion surface is an arc surface, the curvature radius of the arc surface is r2, the radius of the inner ring of the cylinder sleeve is r1, and the minimum clearance distance L=r2-r 1 between the extrusion surface and the cylinder sleeve is more than or equal to 0.005mm and less than or equal to 2mm.

According to another aspect of the present invention, there is provided a heat exchange apparatus comprising the rotary cylinder pump described above.

By adopting the technical scheme, the sealing angle is arranged between at least one side of the liquid suction cavity and/or at least one side of the liquid discharge cavity of the cylinder sleeve and the outer wall surface of the piston assembly, so that the liquid suction cavity and the liquid discharge cavity of the cylinder sleeve are prevented from being communicated, the refrigerant leakage phenomenon can be avoided in the running process of the rotary cylinder pump, and the working efficiency of the rotary cylinder pump is further ensured.

In addition, the rotary cylinder pump provided by the application belongs to a positive displacement pump, namely, the flow of the rotary cylinder pump is irrelevant to pressure difference, so that the problem that the flow of the conventional centrifugal pump and the pressure difference are mutually influenced is solved, the energy efficiency of heat exchange equipment is improved, and in addition, the rotary cylinder pump provided by the application also has certain self-absorption capacity, and the operation reliability of the heat exchange equipment is ensured.

In summary, the rotary cylinder pump provided by the application can obviously improve the energy efficiency, stability and reliability of heat exchange equipment.

Drawings

The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application. In the drawings:

FIG. 1 illustrates a schematic of the mechanism of operation of a rotary cylinder pump according to an alternative embodiment of the present invention;

FIG. 2 is a schematic diagram showing the principle of the mechanism of the operation of the rotary cylinder pump of FIG. 1;

FIG. 3 is a schematic view showing an internal structure of a rotary cylinder pump according to an alternative embodiment of the present invention;

FIG. 4 shows an exploded view of the pump body assembly of the rotary cylinder pump of FIG. 3;

FIG. 5 shows a schematic structural view of a pump body assembly of the rotary cylinder pump of FIG. 3;

FIG. 6 shows a schematic cross-sectional structural view of another view of the pump body assembly of FIG. 3;

FIG. 7 shows a schematic cross-sectional structural view of a cylinder liner of the pump body assembly of FIG. 6;

FIG. 8 shows a schematic structural view of the eccentricity between the cylinder liner and the lower flange of the pump body assembly of FIG. 6;

FIG. 9 shows a schematic structural view of the shaft of the pump body assembly of FIG. 4;

FIG. 10 shows a schematic structural view of the sealing angle between the inner ring of the cylinder liner and the piston assembly of FIG. 6;

fig. 11 is a schematic view showing a state of the rotary cylinder pump in fig. 6 at the start of suction;

Fig. 12 is a schematic view showing a state structure of the rotary cylinder pump in fig. 6 in a suction process;

Fig. 13 is a schematic view showing a state of the rotary cylinder pump in fig. 6 at the end of suction;

FIG. 14 is a schematic view showing the construction of the rotary cylinder pump of FIG. 6 in a state where liquid discharge is started;

FIG. 15 is a schematic view showing a state of the rotary cylinder pump in FIG. 6 in the process of draining liquid;

FIG. 16 is a schematic view showing the construction of the rotary cylinder pump of FIG. 6 at the end of liquid discharge;

Fig. 17 shows a schematic view of a minimum clearance configuration of a head of a piston assembly of the pump body assembly of fig. 6 with an inner ring of a cylinder liner.

Wherein the above figures include the following reference numerals:

1. A pump body assembly; 1a, a liquid inlet channel; 1b, a liquid discharge channel;

2. a housing; 2a, an upper cover; 2b, a lower cover; 2c, a cylinder;

5. a motor assembly;

10. A rotating shaft; 11. a eccentric portion; 12. a shaft body;

20. cylinder sleeve; 21. a buffer tank; 211. a liquid inlet buffer tank; 212. a liquid discharge buffer tank; 22. a liquid suction cavity; 23. a liquid discharge cavity;

30. a piston assembly; 31. a piston sleeve; 311. a limiting channel; 3111. a variable volume chamber; 32. a piston; 322. a through hole; 323. extruding the surface; 3231. decompression diversion trench;

40. a flange; 43. an upper flange; 44. and a lower flange.

Detailed Description

The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.

In order to solve the problems of poor energy efficiency, poor stability and poor reliability of a heat exchange system in the prior art, the invention provides a rotary cylinder pump and heat exchange equipment, wherein the heat exchange equipment comprises the rotary cylinder pump.

As shown in fig. 1 to 17, the rotating shaft 10 is provided with two eccentric parts 11 along the axial direction thereof, the piston assembly 30 comprises a piston sleeve 31 and a piston 32, wherein the piston sleeve 31 is rotatably arranged in the cylinder sleeve 20, the piston sleeve 31 is provided with two limiting channels 311, the two limiting channels 311 are sequentially arranged along the axial direction of the rotating shaft 10, and the extending direction of the limiting channels 311 is perpendicular to the axial direction of the rotating shaft 10; the pistons 32 are provided with through holes 322, the two eccentric parts 11 correspondingly extend into the two through holes 322 of the two pistons 32, the two pistons 32 are correspondingly arranged in the two limiting channels 311 in a sliding way and form a variable-volume cavity 3111, and the rotating shaft 10 rotates to drive the pistons 32 to slide back and forth in the limiting channels 311 and interact with the piston sleeve 31 at the same time, so that the piston sleeve 31 and the pistons 32 rotate in the cylinder sleeve 20; the two eccentric portions 11 have a phase difference of a first included angle A, the eccentric amounts of the two eccentric portions 11 are equal, and the extending directions of the two limiting channels 311 have a limiting difference of a second included angle B, wherein the first included angle A is twice the second included angle B.

By arranging the piston sleeve 31 in a structure form with two limiting channels 311 and correspondingly arranging two pistons 32, two eccentric parts 11 of the rotating shaft 10 correspondingly extend into two through holes 322 of the two pistons 32, meanwhile, the two pistons 32 correspondingly slide in the two limiting channels 311 and form a variable-volume cavity 3111, as a first included angle A between the two eccentric parts 11 is twice as large as a second included angle B between extending directions of the two limiting channels 311, when one of the two pistons 32 is at a dead point position, namely, the driving torque of the eccentric part 11 corresponding to the piston 32 at the dead point position is 0, the piston 32 at the dead point position cannot continue to rotate, and at the moment, the driving torque of the other eccentric part 11 of the two eccentric parts 11 drives the corresponding piston 32 to be the maximum value, so that the eccentric part 11 with the maximum driving torque can normally drive the corresponding piston 32 to rotate, the piston sleeve 31 is driven to rotate through the piston 32, the piston sleeve 31 is driven to rotate continuously through the piston sleeve 31, the piston 32 at the dead point position is driven to rotate continuously, the reliability of the heat exchange pump is ensured, the reliability of the operation of the heat exchange pump is ensured, and the reliability of the operation of the heat exchange pump is avoided.

In addition, the rotary cylinder pump provided by the application can stably run, namely, the energy efficiency of the rotary cylinder pump is higher, the noise is smaller, and therefore, the working reliability of heat exchange equipment is ensured.

In the present application, the first angle a and the second angle B are not zero.

Preferably, the two eccentric portions 11 are arranged at an angle of 180 degrees.

As shown in fig. 4, the rotary shaft 10 further comprises a shaft body 12, the shaft body 12 is provided with a measuring eccentric part 11, the flange 40 comprises an upper flange 43 and a lower flange 44, and the upper flange 43 and the lower flange 44 are respectively arranged at two axial ends of the cylinder sleeve 20

As shown in fig. 4, the piston 32 further has a pressing surface 323, and the pressing surface 323 is provided with a pressure relief guide groove 3231.

As shown in fig. 4, the cylinder liner 20 has a buffer tank 21, and the buffer tank 21 includes a liquid-intake buffer tank 211 and a liquid-discharge buffer tank 212.

As shown in fig. 1 and 2, when the above-described rotary cylinder pump is operated, the rotary shaft 10 rotates about the shaft center O ₀ of the rotary shaft 10; the piston sleeve 31 revolves around the axis O ₀ of the rotating shaft 10, and the axis O ₀ of the rotating shaft 10 and the axis O ₁ of the piston sleeve 31 are eccentrically arranged and have fixed eccentric distances; the first piston 32 moves circularly around the axis O ₀ of the rotating shaft 10, the distance between the center O ₃ of the first piston 32 and the axis O ₀ of the rotating shaft 10 is equal to the eccentric amount of the first eccentric part 11 corresponding to the rotating shaft 10, the eccentric amount is equal to the eccentric distance between the axis O ₀ of the rotating shaft 10 and the axis O ₁ of the piston sleeve 31, the rotating shaft 10 rotates to drive the first piston 32 to move circularly, and the first piston 32 interacts with the piston sleeve 31 and slides back and forth in the limiting channel 311 of the piston sleeve 31; the second piston 32 moves circularly around the axis O ₀ of the rotating shaft 10, the distance between the center O ₄ of the second piston 32 and the axis O ₀ of the rotating shaft 10 is equal to the eccentric amount of the second eccentric portion 11 corresponding to the rotating shaft 10, the eccentric amount is equal to the eccentric distance between the axis O ₀ of the rotating shaft 10 and the axis O ₁ of the piston sleeve 31, the rotating shaft 10 rotates to drive the second piston 32 to move circularly, and the second piston 32 interacts with the piston sleeve 31 and slides reciprocally in the limiting channel 311 of the piston sleeve 31.

The cylinder pump operated in the above manner constitutes a cross slide mechanism, and the operation method adopts the principle of the cross slide mechanism, wherein the two eccentric parts 11 of the rotating shaft 10 are respectively used as a first connecting rod L ₁ and a second connecting rod L ₂, the two limiting channels 311 of the piston sleeve 31 are respectively used as a third connecting rod L ₃ and a fourth connecting rod L ₄, and the lengths of the first connecting rod L ₁ and the second connecting rod L ₂ are equal (please refer to fig. 1).

As shown in fig. 1, a first included angle a is formed between the first link L ₁ and the second link L ₂, and a second included angle B is formed between the third link L ₃ and the fourth link L ₄, wherein the first included angle a is twice the second included angle B.

It should be noted that, in the present application, the first included angle a is 160 degrees to 200 degrees; the second included angle B is 80-100 degrees. In this way, the relationship that the first angle a is twice the second angle B is satisfied.

Preferably, the first included angle a is 160 degrees and the second included angle B is 80 degrees.

Preferably, the first included angle a is 165 degrees and the second included angle B is 82.5 degrees.

Preferably, the first included angle a is 170 degrees and the second included angle B is 85 degrees.

Preferably, the first included angle a is 175 degrees and the second included angle B is 87.5 degrees.

Preferably, the first included angle a is 180 degrees and the second included angle B is 90 degrees.

Preferably, the first included angle a is 185 degrees and the second included angle B is 92.5 degrees.

Preferably, the first included angle a is 190 degrees and the second included angle B is 95 degrees.

Preferably, the first included angle a is 195 degrees and the second included angle B is 97.5 degrees.

As shown in fig. 2, a connecting line between the axis O ₀ of the rotating shaft 10 and the axis O ₁ of the piston sleeve 31 is a connecting line O ₀O₁, a third included angle C is formed between the first connecting rod L ₁ and the connecting line O ₀O₁, and a fourth included angle D is formed between the corresponding third connecting rod L ₃ and the connecting line O ₀ O₁, wherein the third included angle C is twice the fourth included angle D; a fifth included angle E is formed between the second connecting rod L ₂ and the connecting line O ₀ O₁, and a sixth included angle F is formed between the corresponding fourth connecting rod L ₄ and the connecting line O ₀ O₁, wherein the fifth included angle E is twice the sixth included angle F; the sum of the third included angle C and the fifth included angle E is a first included angle A, and the sum of the fourth included angle D and the sixth included angle F is a second included angle B.

Further, the operation method further includes that the rotation angular velocity of the piston 32 with respect to the eccentric portion 11 is the same as the revolution angular velocity of the piston 32 around the axis O ₀ of the rotation shaft 10; the revolution angular velocity of the piston sleeve 31 about the axis O ₀ of the rotary shaft 10 is the same as the rotation angular velocity of the piston 32 with respect to the eccentric portion 11.

Specifically, the axis O ₀ of the rotary shaft 10 corresponds to the rotation centers of the first link L ₁ and the second link L ₂, and the axis O ₁ of the piston sleeve 31 corresponds to the rotation centers of the third link L ₃ and the fourth link L ₄; the two eccentric parts 11 of the rotating shaft 10 are respectively used as a first connecting rod L ₁ and a second connecting rod L ₂, the two limiting channels 311 of the piston sleeve 31 are respectively used as a third connecting rod L ₃ and a fourth connecting rod L ₄, and the lengths of the first connecting rod L ₁ and the second connecting rod L ₂ are equal, so that when the rotating shaft 10 rotates, the eccentric parts 11 on the rotating shaft 10 drive the corresponding pistons 32 to revolve around the axle center O ₀ of the rotating shaft 10, and the pistons 32 can rotate relative to the eccentric parts 11, and the relative rotation speeds of the two pistons are the same, because the first piston 32 and the second piston 32 reciprocate in the two corresponding limiting channels 311 respectively and drive the piston sleeve 31 to do circular motion, the two pistons 32 always have a phase difference of a second included angle B in the motion direction limited by the two limiting channels 311 of the piston sleeve 31, when one of the two pistons 32 is at a dead point position, the eccentric part 11 for driving the other of the two pistons 32 has the maximum driving torque, the eccentric part 11 with the maximum driving torque can normally drive the corresponding piston 32 to rotate, so that the piston sleeve 31 is driven to rotate by the piston 32, and the piston sleeve 31 drives the piston 32 at the dead point position to continuously rotate, so that the stable operation of the rotary cylinder pump is realized, the dead point position of the motion mechanism is avoided, the motion reliability of the rotary cylinder pump is improved, and the working reliability of the heat exchange equipment is ensured.

In the present application, the maximum arm of the driving torque of the eccentric portion 11 is 2e.

In this movement method, the moving track of the piston 32 is a circle, and the circle uses the axis O ₀ of the rotating shaft 10 as the center and uses the connecting line O ₀O₁ as the radius.

In order to solve the problems of poor energy efficiency, poor stability and poor reliability of a heat exchange system in the prior art, the invention constructs a rotary cylinder pump based on the principle of a cross slide block mechanism, and the invention is described below by taking two embodiments as examples.

Example 1

As shown in fig. 3 to 17, the rotary cylinder pump comprises a pump body assembly 1, the pump body assembly 1 comprises a rotary shaft 10, a cylinder sleeve 20 and a piston assembly 30, and the cylinder sleeve 20 are eccentrically arranged and have fixed eccentric distances; the piston assembly 30 is provided with a variable-volume cavity 3111, the piston assembly 30 is rotatably arranged in the cylinder sleeve 20, and the rotating shaft 10 is in driving connection with the piston assembly 30 to change the volume of the variable-volume cavity 3111; the inner wall surface of the cylinder sleeve 20 is provided with a liquid suction cavity 22, and the liquid suction cavity 22 extends along the circumferential direction of the inner wall surface of the cylinder sleeve 20 by a first preset distance to form an arc-shaped liquid suction cavity 22; the inner wall surface of the cylinder liner 20 has a drain chamber 23, and the drain chamber 23 extends a second predetermined distance along the circumferential direction of the inner wall surface of the cylinder liner 20 to form an arc-shaped drain chamber 23, and at least one side of the drain chamber 22 and/or at least one side of the drain chamber 23 has a sealing angle with the outer wall surface of the piston assembly 30.

By arranging the sealing angle between at least one side of the liquid suction cavity 22 and/or at least one side of the liquid discharge cavity 23 of the cylinder sleeve 20 and the outer wall surface of the piston assembly 30, the liquid suction cavity 22 and the liquid discharge cavity 23 of the cylinder sleeve 20 are prevented from being communicated, so that the refrigerant leakage phenomenon can be avoided in the operation process of the rotary cylinder pump, and the working efficiency of the rotary cylinder pump can be further ensured.

In the present application, considering that the inner ring of the cylinder liner 20 is disposed at a distance from the head of the piston 32, in order to avoid communication between the liquid suction chamber 22 and the liquid discharge chamber 23, the sealing angle includes a first sealing angle θ4 and a second sealing angle θ1, as shown in fig. 10, and the first sealing angle θ4 and the second sealing angle θ1 are respectively provided on both circumferential sides of the liquid suction chamber 22, wherein the first sealing angle θ4 is a sealing angle at the start of suction, and the second sealing angle θ1 is a sealing angle at the end of suction. Thus, the liquid suction cavity 22 and the liquid discharge cavity 23 are favorably prevented from being communicated, so that the leakage phenomenon of the refrigerant is avoided, and the working efficiency of the rotary cylinder pump is further ensured.

Further, the sealing angles include a third sealing angle θ3 and a fourth sealing angle θ2, and the two sides of the drain cavity 23 in the circumferential direction have the third sealing angle θ3 and the fourth sealing angle θ2, respectively, where the third sealing angle θ3 is a sealing angle at the end of the discharge, and the fourth sealing angle θ2 is a sealing angle at the beginning of the discharge.

Specifically, since the working medium of the rotary cylinder pump is a liquid refrigerant, the liquid refrigerant has incompressible characteristics of conventional liquid and also has volatile gasification characteristics, as shown in fig. 10, when the rotary cylinder pump is at the 0-degree position, the fourth sealing angle θ3 is closest to the liquid discharge cavity 23, the first sealing angle θ4 is closest to the liquid suction cavity 22, a pressure difference exists between the first sealing angle θ4 and the liquid suction cavity, that is, an inlet-outlet pressure difference of the rotary cylinder pump, and in addition, a gap distance exists between the head of the piston 32 at the 0-degree position and the inner ring of the cylinder sleeve 20, if the sealing angle is not set, the liquid suction cavity 22 and the liquid discharge cavity 23 are communicated, so that the working efficiency of the rotary cylinder pump is seriously affected, and based on the fact that the corresponding first sealing angle θ4 and fourth sealing angle θ3 are set from the aspect of reducing leakage.

However, when the sealing angle is larger, the sealing performance is better, and certain negative effects are generated at the same time:

In the angular range of the third sealing angle θ3, considering that the refrigerant in the variable volume chamber 3111 is not communicated with the liquid discharge chamber 23, a certain overcompression is generated, the larger the third sealing angle θ3 is, the better the sealing property is, but the more serious the overcompression is, the third sealing angle θ3 is set to satisfy: and the structural form of theta 3 is more than or equal to 0 and less than or equal to 10 degrees.

Preferably, the third sealing angle θ3 satisfies: theta 3 is more than or equal to 1 degree and less than or equal to 5 degrees.

In the angular range of the first sealing angle θ4, the volume of the variable volume chamber 3111 gradually increases, but at this time, the pressure in the gap between the head of the piston 32 and the inner ring of the cylinder liner 20 is reduced without communicating with the liquid suction chamber 22, and the residual refrigerant volatilizes and vaporizes, thereby generating bubbles; when the head of the piston 32 is separated from the angle range of the first sealing angle θ4 and is communicated with the liquid suction cavity 22, the pressure is rapidly increased, the vaporized refrigerant is liquefied instantaneously, the bubbles disappear, cavitation is very easy to occur in the whole process, and thus the working reliability of the cylinder rotating pump is seriously affected, and the first sealing angle θ4 is set to satisfy the following conditions through researches: and the structural form of theta 4 is more than or equal to 0 and less than or equal to 10 degrees.

Preferably, the first sealing angle θ4 satisfies: theta 4 is more than or equal to 1 degree and less than or equal to 5 degrees.

As shown in fig. 10, when the position is near 180 °, the second sealing angle θ1 side is communicated with the liquid suction cavity 22, the fourth sealing angle θ2 side is communicated with the liquid discharge cavity 23, and a pressure difference exists between the two, that is, an inlet-outlet pressure difference, and at this time, the distance between the head of the piston 32 and the inner ring of the cylinder liner 20 is the maximum, if the sealing distance is not set, the refrigerant in the liquid discharge cavity 23 leaks into the variable volume cavity 3111, the pressure of the refrigerant in the variable volume cavity 3111 rises, and then the refrigerant enters the liquid suction cavity 22, so that the liquid discharge amount of the cylinder pump is seriously affected, and the working efficiency of the cylinder pump is reduced, and based on this, the second sealing angle θ1 and the fourth sealing angle θ2 are set.

In the second sealing angle θ1, the variable volume chamber 3111 is separated from the liquid suction chamber 22, and the volume of the variable volume chamber 3111 is continuously increased between θ1 and 180 °, which may reduce the liquid pressure, thereby generating vaporization of the refrigerant and formation of bubbles; after 180 °, the volume of the variable volume chamber 3111 is reduced, the pressure is increased, the vaporized refrigerant is washed and liquefied, the refrigerant bubble is broken, cavitation occurs, the working reliability of the rotary cylinder pump is seriously affected, the larger the second sealing angle θ1 is, the better the sealing property is, but the more serious the cavitation effect is, and the second sealing angle θ1 is set to satisfy: and the structural form of theta 1 is more than or equal to 0 and less than or equal to 10 degrees.

Preferably, the second sealing angle θ1 satisfies: theta 1 is more than or equal to 1 degree and less than or equal to 5 degrees.

In the angle range of the fourth sealing angle θ2, the volume of the variable volume chamber 3111 is gradually reduced, but the variable volume chamber 3111 at this time is not communicated with the liquid discharge chamber 23, so that the liquid is sealed in the variable volume chamber 3111, the pressure is continuously increased, the power consumption of the rotary cylinder pump is increased, the working efficiency of the rotary cylinder pump is seriously affected, and the fourth sealing angle θ2 is set to satisfy: and the structural form of theta 2 is more than or equal to 0 and less than or equal to 10 degrees.

Preferably, the fourth sealing angle θ2 satisfies: theta 2 is more than or equal to 1 degree and less than or equal to 5 degrees.

In this embodiment, since the fourth sealing angle θ2 is directly connected to the liquid discharge chamber 23 and is sealed at high pressure, the sealing requirement at the fourth sealing angle θ2 is greater than θ1, and 0 degree is less than or equal to θ2- θ1 is less than or equal to 5 degrees, and similarly 0 degree is less than or equal to θ3- θ4 is less than or equal to 5 degrees.

As shown in fig. 11 to 16, the piston 32 rotates relative to the cylinder liner 20 while reciprocating in the limiting passage 311, fig. 11 is a schematic structural diagram of the rotary cylinder pump in a state where liquid suction starts, fig. 12 is a schematic structural diagram of the rotary cylinder pump in a state where liquid suction ends, fig. 13 is a schematic structural diagram of the rotary cylinder pump in a state where liquid suction ends, fig. 14 is a schematic structural diagram of the rotary cylinder pump in a state where liquid discharge starts, fig. 15 is a schematic structural diagram of the rotary cylinder pump in a state where liquid discharge ends, and fig. 16 is a schematic structural diagram of the rotary cylinder pump in a state where liquid discharge ends.

In the embodiment, the rotary cylinder pump has the characteristics of four variable volume chambers 3111 of the single cylinder liner 20, and the four variable volume chambers 3111 operate synchronously, but the working states of the four variable volume chambers 3111 have a phase difference of 90 °. For a single variable volume chamber 3111, the first 180 completes the inhalation process and the last 180 completes the expelling process. In the liquid suction process, the volume change rate of the volume-changing cavity 3111 is gradually increased within the range of 0-90 degrees, and the volume change rate of 180 degrees is 0; in the discharging process, the volume change rate is gradually increased within the range of 180-270 degrees, gradually decreased within the range of 270-360 degrees and is 0 at 360 degrees. After the volume change rates of the four variable volume chambers 3111 are combined, the combined volume change rates are alternately changed with a period of 90 °.

The instantaneous rate of the inlet fluid of the rotary cylinder pump is the volume change rate divided by the sectional area of the intake passage 1a, and when the volume change rate is constant, the larger the sectional area of the intake passage 1a is, the smaller the average fluid rate is. A flow rate change rule; similarly, the instantaneous rate of the outlet fluid of the cylinder pump is the volume change rate divided by the cross-sectional area of the drain passage 1b, and the larger the cross-sectional area of the drain passage 1b is, the smaller the average fluid rate is. The flow rate change law.

As shown in fig. 10, the piston assembly 30 has a piston sleeve 31, the piston sleeve 31 is rotatably disposed in the cylinder liner 20, and the sealing angles include a first sealing angle θ4, a second sealing angle θ1, a third sealing angle θ3, and a fourth sealing angle θ2, wherein the piston assembly 30 has the first sealing angle θ4 with the suction start side of the liquid suction chamber 22, the piston assembly 30 has the second sealing angle θ1 with the suction end side of the liquid suction chamber 22, the piston assembly 30 has the third sealing angle θ2 with the discharge start side of the liquid discharge chamber 23, and the piston assembly 30 has the fourth sealing angle θ3 with the discharge end side of the liquid discharge chamber 23; and the first sealing angle theta 4, the second sealing angle theta 1 are determined by the positions of the piston sleeve 31 and the two ends of the arc-shaped liquid suction cavity 22, and the third sealing angle theta 2 and the fourth sealing angle theta 3 are determined by the positions of the piston sleeve 31 and the two ends of the arc-shaped liquid discharge cavity 23.

As shown in fig. 10, the piston assembly 30 has a piston sleeve 31, the piston sleeve 31 is rotatably provided in the cylinder liner 20, the pump body assembly 1 has a liquid sucking state and a liquid discharging state according to the rotational position change of the piston sleeve 31, the piston sleeve 31 has a suction start position, a suction end position, a discharge start position, and a discharge end position, and when the piston sleeve 31 is in the suction start position, the variable volume chamber 3111 starts to communicate with the liquid sucking chamber 22; when the piston sleeve 31 is at the suction end position, the variable volume chamber 3111 ends communication with the suction chamber 22; when the piston housing 31 is at the discharge start position, the variable volume chamber 3111 starts communication with the drain chamber 23; when the piston sleeve 31 is at the discharge end position, the variable volume chamber 3111 ends communication with the drain chamber 23.

As shown in fig. 3 to 17, the cylinder liner 20 has a liquid intake passage 1a and a liquid discharge passage 1b, and the liquid intake passage 1a and the liquid discharge passage 1b are disposed 180 ° opposite to each other, the liquid intake passage 1a communicating with the liquid suction chamber 22, and the liquid discharge passage 1b communicating with the liquid discharge chamber 23. Therefore, the rotary cylinder pump provided by the application belongs to a positive displacement pump, namely, the flow rate of the rotary cylinder pump is irrelevant to the pressure difference, and the problem that the flow rate and the pressure difference of the conventional centrifugal pump are mutually influenced is solved, so that the energy efficiency of heat exchange equipment is improved, and in addition, the rotary cylinder pump provided by the application also has certain self-absorption capacity, and the operation reliability of the heat exchange equipment is ensured.

As shown in fig. 4, the stopper passage 311 has a set of oppositely disposed first sliding surfaces in sliding 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 323 toward the end of the stopper passage 311, the pressing surface 323 serves as the head of the piston 32, the two second sliding surfaces are connected by the pressing surface 323, and the pressing surface 323 faces the variable volume chamber 3111.

As shown in fig. 17, the extrusion surface 323 is an arc surface, the curvature radius of the arc surface is r2, the radius of the inner ring of the cylinder liner 20 is r1, and the minimum clearance distance l=r2-r 1 between the extrusion surface 323 and the cylinder liner 20 is equal to or greater than 0.005mm and equal to or less than 2mm. Thus, the liquid suction cavity 22 and the liquid discharge cavity 23 are prevented from being communicated, so that the phenomenon of refrigerant leakage in the operation process of the rotary cylinder pump is prevented.

Example two

It should be noted that, the difference between the present embodiment and the first embodiment is that the piston assembly 30 includes a piston sleeve 31 and a piston 32, wherein the piston sleeve 31 is rotatably disposed in the cylinder sleeve 20, the piston sleeve 31 has a limiting channel 311, and an extending direction of the limiting channel 311 is perpendicular to an axial direction of the rotating shaft 10; the piston 32 is slidably disposed in the limiting channel 311 to form a variable volume cavity 3111, the variable volume cavity 3111 is located in a sliding direction of the piston 32, the piston 32 has a sliding groove, during rotation of the rotating shaft 10, the piston 32 slides relative to the rotating shaft 10, so that the rotating shaft 10 is slidably matched with a groove wall surface of the sliding groove, and the piston 32 rotates along with the rotating shaft 10 under driving of the rotating shaft 10 and simultaneously slides reciprocally in the piston sleeve 31 along an axial direction perpendicular to the rotating shaft 10.

It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.

The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present invention unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not 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 figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.

Spatially relative terms, such as "above … …," "above … …," "upper surface on … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

It should be noted that the terms "first," "second," and the like in the description and the claims of the present application and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate such that embodiments of the application described herein may be implemented in sequences other than those illustrated or otherwise described herein.

The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. The rotary cylinder pump is characterized by comprising a pump body assembly (1), wherein the pump body assembly (1) comprises:

a rotating shaft (10);

the cylinder sleeve (20) is eccentrically arranged with the cylinder sleeve (20) and the eccentric distance is fixed;

-a piston assembly (30), the piston assembly (30) having a variable volume chamber (3111), the piston assembly (30) being rotatably arranged within the cylinder liner (20), and the spindle (10) being in driving connection with the piston assembly (30) for varying the volume of the variable volume chamber (3111);

The inner wall surface of the cylinder sleeve (20) is provided with a liquid suction cavity (22), and the liquid suction cavity (22) extends along the circumferential direction of the inner wall surface of the cylinder sleeve (20) for a first preset distance to form an arc-shaped liquid suction cavity (22); the inner wall surface of the cylinder sleeve (20) is provided with a liquid draining cavity (23), the liquid draining cavity (23) extends along the circumferential direction of the inner wall surface of the cylinder sleeve (20) for a second preset distance to form an arc-shaped liquid draining cavity (23), and at least one side of the liquid draining cavity (22) and/or at least one side of the liquid draining cavity (23) and the outer wall surface of the piston assembly (30) are provided with sealing angles.

2. The rotary cylinder pump according to claim 1, wherein the sealing angle includes a first sealing angle θ4 and a second sealing angle θ1, and both circumferential sides of the liquid suction chamber (22) have the first sealing angle θ4 and the second sealing angle θ1, respectively, wherein the first sealing angle θ4 is a sealing angle at the start of suction and the second sealing angle θ1 is a sealing angle at the end of suction.

3. The rotary cylinder pump as claimed in claim 2, wherein,

The first sealing angle θ4 satisfies: theta 4 is more than or equal to 0 and less than or equal to 10 degrees; and/or the number of the groups of groups,

The second sealing angle θ1 satisfies: θ1 is more than or equal to 0 and less than or equal to 10 degrees.

4. The rotary cylinder pump as claimed in claim 3, wherein,

The first sealing angle θ4 satisfies: theta 4 is more than or equal to 1 degree and less than or equal to 5 degrees; and/or the number of the groups of groups,

The second sealing angle θ1 satisfies: theta 1 is more than or equal to 1 degree and less than or equal to 5 degrees.

5. The rotary cylinder pump according to claim 1, wherein the sealing angle includes a third sealing angle θ3 and a fourth sealing angle θ2, and both circumferential sides of the liquid discharge chamber (23) have the third sealing angle θ3 and the fourth sealing angle θ2, respectively, wherein the third sealing angle θ3 is a sealing angle at the end of discharge, and the fourth sealing angle θ2 is a sealing angle at the beginning of discharge.

6. The rotary cylinder pump as claimed in claim 5, wherein,

The third sealing angle θ3 satisfies: theta 3 is more than or equal to 0 and less than or equal to 10 degrees; and/or the number of the groups of groups,

The fourth sealing angle θ2 satisfies: θ2 is more than or equal to 0 and less than or equal to 10 degrees.

7. The rotary cylinder pump as claimed in claim 6, wherein,

The third sealing angle θ3 satisfies: theta 3 is more than or equal to 1 degree and less than or equal to 5 degrees; and/or the number of the groups of groups,

The fourth sealing angle θ2 satisfies: theta 2 is more than or equal to 1 degree and less than or equal to 5 degrees.

8. The rotary cylinder pump as claimed in claim 1, wherein the piston assembly (30) has a piston sleeve (31), the piston sleeve (31) being rotatably disposed within the cylinder liner (20), the sealing angles comprising a first sealing angle θ4, a second sealing angle θ1, a third sealing angle θ3, a fourth sealing angle θ2,

Wherein a suction start side of the piston assembly (30) and the liquid suction cavity (22) has a first sealing angle theta 4, a suction end side of the piston assembly (30) and the liquid suction cavity (22) has a second sealing angle theta 1, a discharge start side of the piston assembly (30) and the liquid discharge cavity (23) has a third sealing angle theta 2, and a discharge end side of the piston assembly (30) and the liquid discharge cavity (23) has a fourth sealing angle theta 3;

And the first sealing angle theta 4 and the second sealing angle theta 1 are determined by the positions of the piston sleeve (31) and the two ends of the arc-shaped liquid suction cavity (22), and the third sealing angle theta 2 and the fourth sealing angle theta 3 are determined by the positions of the piston sleeve (31) and the two ends of the arc-shaped liquid discharge cavity (23).

9. The rotary cylinder pump as claimed in claim 8, wherein,

Theta 2-theta 1 is more than or equal to 0 degree and less than or equal to 5 degrees; and/or

0°≤θ3-θ4≤5°。

10. The rotary cylinder pump according to claim 1, wherein the piston assembly (30) has a piston sleeve (31), the piston sleeve (31) is rotatably provided in the cylinder liner (20), the pump body assembly (1) has a liquid sucking state and a liquid discharging state according to a positional change of rotation of the piston sleeve (31), the piston sleeve (31) has a suction start position, a suction end position, a discharge start position, and a discharge end position,

-Said variable volume chamber (3111) is brought into communication with said suction chamber (22) when said piston bush (31) is in said suction start position;

-said variable volume chamber (3111) is in end communication with said suction chamber (22) when said piston sleeve (31) is in said end of suction position;

When the piston bush (31) is at the discharge start position, the variable volume chamber (3111) starts communication with the drain chamber (23);

when the piston bush (31) is at the discharge end position, the variable volume chamber (3111) is in end communication with the drain chamber (23).

11. The rotary cylinder pump according to any one of claims 1 to 10, characterized in that the cylinder liner (20) has a liquid intake channel (1 a) and a liquid discharge channel (1 b), and the liquid intake channel (1 a) and the liquid discharge channel (1 b) are disposed 180 ° opposite, the liquid intake channel (1 a) being in communication with the liquid suction chamber (22), the liquid discharge channel (1 b) being in communication with the liquid discharge chamber (23).

12. The rotary cylinder pump as claimed in claim 1, wherein the piston assembly (30) comprises:

The piston sleeve (31) is rotatably arranged in the cylinder sleeve (20), the piston sleeve (31) is provided with a limiting channel (311), and the extending direction of the limiting channel (311) is perpendicular to the axial direction of the rotating shaft (10);

the piston (32), piston (32) slip sets up in spacing passageway (311) in order to form become volume chamber (3111), just become volume chamber (3111) and be located in the slip direction of piston (32), piston (32) have the groove of sliding, pivot (10) pivoted in-process, piston (32) for pivot (10) slip, so that pivot (10) with the cell wall sliding fit in groove of sliding, just piston (32) are driven by pivot (10) follow pivot (10) rotates and simultaneously along being perpendicular to pivot (10) axial reciprocating sliding in piston sleeve (31).

13. A rotary cylinder pump according to claim 1, wherein the rotary shaft (10) is provided with two eccentric parts (11) in its axial direction, and the piston assembly (30) comprises:

The piston sleeve (31) is rotatably arranged in the cylinder sleeve (20), the piston sleeve (31) is provided with two limiting channels (311), the two limiting channels (311) are sequentially arranged along the axial direction of the rotating shaft (10), and the extending direction of the limiting channels (311) is perpendicular to the axial direction of the rotating shaft (10);

The piston (32), piston (32) have through-hole (322), piston (32) are two, two eccentric part (11) correspond to stretch into two in through-hole (322) of piston (32), two piston (32) correspond the slip setting in two spacing passageway (311) and form become volume cavity (3111), pivot (10) rotate in order to drive piston (32) in spacing passageway (311) reciprocating sliding simultaneously with piston sleeve (31) interact, so that piston sleeve (31) piston (32) are in cylinder liner (20) internal rotation.

14. The rotary cylinder pump as claimed in claim 13, characterized in that the two eccentric portions (11) have a phase difference of a first angle a, the eccentric amounts of the two eccentric portions (11) are equal, and the two limiting passages (311) have a limiting difference of a second angle B between the extending directions of the two limiting passages (311), wherein the first angle a is twice the second angle B.

15. A rotary cylinder pump according to claim 13, characterized in that the two eccentric parts (11) are arranged at an angle of 180 degrees.

16. The rotary cylinder pump according to claim 12 or 13, characterized in that the limiting channel (311) has a set of oppositely disposed first sliding surfaces in sliding contact with the piston (32), the piston (32) has a second sliding surface cooperating with the first sliding surface, the piston (32) has a pressing surface (323) towards the end of the limiting channel (311), the pressing surface (323) acts as a head of the piston (32), the two second sliding surfaces are connected by the pressing surface (323), and the pressing surface (323) faces the variable volume chamber (3111).

17. The rotary cylinder pump as claimed in claim 16, wherein the pressing surface (323) is an arc surface, the radius of curvature of the arc surface is r2, the radius of the inner ring of the cylinder liner (20) is r1, and the minimum clearance distance l=r2-r 1 between the pressing surface (323) and the cylinder liner (20), wherein L is 0.005 mm.ltoreq.2 mm.

18. A heat exchange apparatus comprising a rotary cylinder pump as claimed in any one of claims 1 to 17.