CN222276942U - Pump body assembly, rotary cylinder pump and heat exchange equipment - Google Patents

Abstract

The utility model provides a pump body assembly, a rotary cylinder pump and heat exchange equipment, wherein the pump body assembly comprises a rotating shaft, a cylinder sleeve, a piston assembly and two flanges, the rotating shaft and the cylinder sleeve are eccentrically arranged, the eccentric distance is fixed, the piston assembly is provided with a variable-volume cavity, the piston assembly is rotatably arranged in the cylinder sleeve, the rotating shaft and the piston assembly are in driving connection, a liquid suction port and liquid discharge ports are arranged on the cylinder sleeve, the two flanges are respectively arranged at two axial ends of the cylinder sleeve, the two liquid discharge ports are arranged at intervals along the axial direction of the cylinder sleeve, at least one liquid discharge port in the two liquid discharge ports penetrates through the axial end face of the cylinder sleeve, and a liquid discharge channel is formed in the flange at least positioned at one side of the axial end face of the liquid discharge port, which penetrates through the cylinder sleeve, and is used for communicating with the liquid discharge ports at the same side. The utility model solves the problems of the prior art that the resistance of fluid discharge in the cylinder sleeve of the fluorine pump is large and the efficiency of the fluorine pump is not improved.

Description

Pump body assembly, rotary cylinder pump and heat exchange equipment

Technical Field

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

Background

In the fields of data centers, machine room air conditioners and the like, a liquid pump is generally adopted to replace a compressor, a driving refrigerant is operated in an air conditioning system, the energy efficiency is higher than that of a conventional air conditioning system, a system using the pump to drive the refrigerant is called a fluorine pump system in the industry, and a pump driving the refrigerant to operate is called a fluorine pump.

However, the resistance of the fluid in the cylinder sleeve of the existing fluorine pump to discharge is large, which is not beneficial to improving the efficiency of the fluorine pump.

Disclosure of utility model

The utility model mainly aims to provide a pump body assembly, a rotary cylinder pump and heat exchange equipment, so as to solve the problems that in the prior art, the resistance of fluid in a cylinder sleeve of a fluorine pump is large, and the efficiency of the fluorine pump is not improved.

According to the pump body assembly, the cylinder sleeve is provided with a liquid suction port and a liquid discharge port, the liquid suction port is communicated with the volume-variable cavity and used for conveying refrigerant into the volume-variable cavity, the liquid discharge port is communicated with the volume-variable cavity and used for discharging the refrigerant in the volume-variable cavity through the liquid discharge port, the two flanges are respectively arranged at two axial ends of the cylinder sleeve, the liquid discharge ports are arranged at intervals along the axial direction of the cylinder sleeve, at least one liquid discharge port penetrates through the axial end face of the cylinder sleeve, a liquid discharge channel is formed in the flange at one side of the axial end face of the cylinder sleeve, and the liquid discharge channel is used for being communicated with the liquid discharge port at the same side.

Further, the drain channel extends in the axial direction of the flange.

Further, at least one of the two liquid discharge ports penetrates through the outer peripheral surface of the cylinder sleeve, or at least one of the two liquid discharge ports does not penetrate through the outer peripheral surface of the cylinder sleeve.

Further, the projection of the contour line of the liquid discharge channel on the axial direction of the flange is one of a circle, a rectangle, an arc and a special shape.

Further, the projection of the contour line of the liquid discharge channel on the axial direction of the flange is circular, and the channel diameter D1 of the liquid discharge channel and the width W1 of the liquid discharge port are satisfied that D1 is less than or equal to W1.

Further, the contour line projection of the drain channel in the axial direction of the flange is located outside the inner circle of the cylinder sleeve, or the part of the contour line projection of the drain channel in the axial direction of the flange is located inside the inner circle of the cylinder sleeve, and the other part of the contour line projection of the drain channel in the axial direction of the flange is located outside the inner circle of the cylinder sleeve, or the contour line projection of the drain channel in the axial direction of the flange is located inside the inner circle of the cylinder sleeve.

Further, when the portion of the drain passage projected on the axial direction of the flange is located inside the inner circle of the cylinder liner, or when the portion of the drain passage projected on the axial direction of the flange is located inside the inner circle of the cylinder liner, the portion of the drain passage projected on the axial direction of the flange is located outside the contour of the variable volume chamber.

Further, when the part of the profile line projection of the drain channel in the axial direction of the flange is located inside the inner circle of the cylinder sleeve, or when the profile line projection of the drain channel in the axial direction of the flange is located inside the inner circle of the cylinder sleeve, the profile line projection of the drain channel in the axial direction of the flange is located outside the profile line of the shaft hole on the flange, and a first preset distance L is provided between the drain channel and the hole edge of the shaft hole.

Further, a ratio L/D2 between the first preset distance L and a hole diameter D2 of the shaft hole is >0.3.

Further, the ratio of the height H2 of the connecting part between the two liquid discharging ports in the axial direction of the cylinder sleeve to the height H1 of the cylinder sleeve in the axial direction of the cylinder sleeve is in the range of 0.1-0.5.

Further, the ratio of the depth H3 of the liquid outlet positioned above in the axial direction of the cylinder sleeve to the height H1 of the cylinder sleeve in the axial direction is in the range of 0.1-0.4.

Further, the ratio of the depth H4 of the liquid outlet positioned below in the axial direction of the cylinder sleeve to the height H1 of the cylinder sleeve in the axial direction of the cylinder sleeve is in the range of 0.1-0.4.

The piston is provided with through holes, the two eccentric parts correspondingly extend into the two through holes of the two pistons, the two pistons are correspondingly arranged in the two limiting channels in a sliding mode and form a variable-volume cavity, the variable-volume cavity is located in the sliding direction of the piston, and the rotating shaft rotates to drive the piston to slide back and forth in the limiting channels and interact with the piston sleeve to enable the piston sleeve and the piston to rotate in the cylinder sleeve.

Further, the ratio of the height H2 of the connection between the two liquid discharge ports in the axial direction of the cylinder sleeve to the height H _q2 of the connection between the two limiting channels in the axial direction of the piston sleeve is in the range of 0.9-3.

Further, the ratio of the height H2 of the connection between the two liquid discharge ports in the axial direction of the cylinder sleeve to the height H _q2 of the connection between the two limiting channels in the axial direction of the piston sleeve is 1.1-1.2.

Further, the width W1 of the liquid outlet and the length L _qc of the channel wall of the limiting channel meet the condition that W1 is less than or equal to L _qc.

Further, the width W1 of the liquid outlet and the length L _qc of the channel wall of the limiting channel meet the condition that the value range of L _qc -W1 is 2-6 mm.

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

Further, the two eccentric portions are disposed 180 ° opposite to each other.

According to another aspect of the utility model, a rotary cylinder pump is provided, comprising a pump body assembly, wherein the pump body assembly is the pump body assembly.

According to another aspect of the utility model, there is provided a heat exchange device comprising a rotary cylinder pump, the rotary cylinder pump being the rotary cylinder pump described above.

By adopting the technical scheme of the utility model, at least one liquid outlet of the two liquid outlets penetrates through the axial end face of the cylinder sleeve, and meanwhile, the flange at least positioned on one side of the liquid outlet penetrating through the axial end face of the cylinder sleeve is provided with the liquid outlet channel, and the liquid outlet channel is used for being communicated with the liquid outlet on the same side, so that the liquid outlet channel on the flange can assist in discharging fluid, thereby being beneficial to reducing the resistance in the fluid discharging process and further being beneficial to improving the efficiency of the cylinder rotating pump.

Drawings

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

FIG. 1 shows a schematic structural view of a pump body assembly according to an alternative embodiment of the present utility model;

FIG. 2 shows a schematic cross-sectional view of the pump body assembly of FIG. 1;

FIG. 3 shows a schematic view of the pump body assembly of FIG. 1 with the upper flange omitted;

FIG. 4 shows a schematic structural view of a cylinder liner of the pump body assembly of FIG. 3;

FIG. 5 shows a schematic structural view from a top view of the pump body assembly of FIG. 1, showing the contour lines of the drain passages all located outside the inner circle of the cylinder liner;

FIG. 6 shows a schematic structural view from a top view of the pump body assembly of FIG. 1, showing the contoured line portion of the drain passage within the inner circle of the cylinder liner;

FIG. 7 is a schematic diagram of the pump body assembly of FIG. 1 from a top view showing the drain passage contour lines all within the inner circle of the cylinder liner;

FIG. 8 shows a schematic diagram of the positional relationship between the contour line of the liquid discharge passage in FIG. 6, FIG. 7, which is partially or entirely located inside the inner circle of the cylinder liner, the contour line V of the variable volume chamber, and the flange shaft hole T;

FIG. 9 shows a schematic structural view of an upper flange of a pump body assembly according to a first embodiment of the present utility model;

FIG. 10 shows a schematic structural view of an upper flange of a pump body assembly according to a second embodiment of the present utility model;

FIG. 11 shows a schematic structural view of an upper flange of a pump body assembly according to a third embodiment of the present utility model;

FIG. 12 shows a schematic structural view of an upper flange of a pump body assembly according to a fourth embodiment of the present utility model;

FIG. 13 shows a schematic view of the structure of the lower flange of the pump body assembly according to the first embodiment of the present utility model;

FIG. 14 shows a schematic structural view of a lower flange of a pump body assembly according to a second embodiment of the present utility model;

FIG. 15 shows a schematic structural view of a lower flange of a pump body assembly according to a third embodiment of the present utility model;

FIG. 16 shows a schematic structural view of a lower flange of a pump body assembly according to a fourth embodiment of the present utility model;

fig. 17 shows a schematic structural view of a pump body assembly according to a second embodiment of the present utility model;

FIG. 18 shows a schematic cross-sectional view of the pump body assembly of FIG. 17;

FIG. 19 shows a schematic structural view of a cylinder liner of the pump body assembly of FIG. 17;

FIG. 20 shows a schematic view of the structure of the suction port side of the cylinder liner of FIG. 19;

FIG. 21 shows a schematic structural view of the cylinder liner of FIG. 20 from a top view;

fig. 22 shows a schematic structure of the Y view in fig. 21;

FIG. 23 shows a schematic structural view of a piston sleeve of a pump body assembly according to an alternative embodiment of the utility model;

FIG. 24 shows a schematic cross-sectional structural view of the piston sleeve of FIG. 23 from the Z-Z perspective;

Fig. 25 shows a schematic structural view of the piston sleeve of fig. 23 from a top view.

Wherein the above figures include the following reference numerals:

10. 11, eccentric part;

20. cylinder sleeve; 21, a liquid suction port, 22, a liquid discharge port, 23, a buffer groove, 24 and a liquid suction groove;

30. the piston comprises a piston assembly, a piston sleeve, a limiting channel, a 3111 variable-volume cavity, a piston 32 and a piston;

40. Flange, 42, upper flange, 43, lower flange, 41, drain channel, 411, upper drain channel, 412, lower drain channel.

Detailed Description

The following description of the embodiments of the present utility model 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 utility model, 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 utility model, its application, or uses. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.

In order to solve the problems that in the prior art, the resistance of fluid in a cylinder sleeve of a fluorine pump is large and the efficiency of the fluorine pump is not improved, the utility model provides a pump body assembly, a rotary cylinder pump and heat exchange equipment.

Example 1

As shown in fig. 1 to 16, the pump body assembly comprises a rotating shaft 10, a cylinder sleeve 20, a piston assembly 30 and two flanges 40, wherein the rotating shaft 10 and the cylinder sleeve 20 are eccentrically arranged, the eccentric distance is fixed, the piston assembly 30 is provided with a variable-volume cavity 3111, the piston assembly 30 is rotatably arranged in the cylinder sleeve 20, the rotating shaft 10 is in driving connection with the piston assembly 30 to change the volume of the variable-volume cavity 3111, the cylinder sleeve 20 is provided with a liquid suction port 21 and a liquid discharge port 22, the liquid suction port 21 is communicated with the variable-volume cavity 3111 and conveys refrigerant into the variable-volume cavity 3111, the liquid discharge port 22 is communicated with the variable-volume cavity 3111 and discharges the refrigerant in the variable-volume cavity 3111 through the liquid discharge port 22, the two flanges 40 are respectively arranged at two axial ends of the cylinder sleeve 20, the two liquid discharge ports 22 are arranged at intervals along the axial direction of the cylinder sleeve 20, at least one liquid discharge port 22 penetrates through the axial end face of the cylinder sleeve 20, a liquid discharge channel 41 is arranged on the flange 40 at least on one axial end face side of the liquid discharge port 22, which penetrates the cylinder sleeve 20, and the liquid discharge channel 41 is used for being communicated with the liquid discharge port 22 on the same side.

Through the axial end face of the cylinder sleeve 20 is penetrated through at least one liquid outlet 22 in the two liquid outlets 22, meanwhile, a liquid outlet channel 41 is formed in the flange 40 at one side of the axial end face of the cylinder sleeve 20, which is penetrated through at least the liquid outlet 22, the liquid outlet channel 41 is used for being communicated with the liquid outlet 22 at the same side, so that the liquid outlet channel 41 on the flange 40 can assist in discharging fluid, and therefore resistance in the fluid discharging process is reduced, and further efficiency of the rotary cylinder pump is improved.

In the present embodiment, the drain passage 41 extends in the axial direction of the flange 40.

As shown in fig. 4, the inner wall surface of the cylinder sleeve 20 is provided with a liquid suction groove 24, the cylinder sleeve 20 is also provided with a buffer groove 23, and the liquid suction groove 24 is communicated with the liquid suction port 21 through the buffer groove 23.

Alternatively, at least one liquid discharge port 22 of the two liquid discharge ports 22 penetrates the outer circumferential surface of the cylinder liner 20.

Alternatively, at least one liquid discharge port 22 of the two liquid discharge ports 22 does not penetrate the outer circumferential surface of the cylinder liner 20.

In the present embodiment, both the liquid discharge ports 22 penetrate the outer peripheral surface of the cylinder liner 20.

In the present embodiment, the projection of the contour line of the drain channel 41 in the axial direction of the flange 40 is one of a circle, a rectangle, an arc, and a special shape.

In this embodiment, the flange 40 includes an upper flange 42 and a lower flange 43, the drain channel 41 includes an upper drain channel 411 and a lower drain channel 412, wherein the upper flange 42 is provided with the upper drain channel 411, and the lower flange 43 is provided with the lower drain channel 412.

As shown in fig. 7, the letter Q represents the geometric center of the cylinder liner 20, the letter M represents the geometric center of the shaft body portion of the rotary shaft 10, and the letter U represents the geometric center of the eccentric portion 11.

As shown in fig. 9 to 12, the projection of the contour line of the upper drain passage 411 in the axial direction of the upper flange 42 is one of a circle, a rectangle, an arc, and a special shape.

As shown in fig. 13 to 16, the projection of the contour line of the lower drain passage 412 in the axial direction of the lower flange 43 is one of a circle, a rectangle, an arc, and a special shape.

Alternatively, the projection of the contour line of the drain passage 41 in the axial direction of the flange 40 is circular, and it is satisfied that D1. Ltoreq.W1 (see FIG. 21) is satisfied between the passage diameter D1 of the drain passage 41 and the width W1 of the drain port 22.

As shown in fig. 5, the contour projection of the drain passage 41 in the axial direction of the flange 40 is located outside the inner circle of the cylinder liner 20.

As shown in fig. 6, a portion of the drain passage 41 projected in the axial direction of the flange 40 is located inside the inner circle of the cylinder liner 20, and another portion of the drain passage 41 projected in the axial direction of the flange 40 is located outside the inner circle of the cylinder liner 20.

As shown in fig. 7, the contour projection of the drain passage 41 in the axial direction of the flange 40 is located inside the inner circle of the cylinder liner 20.

As shown in fig. 8, when the portion of the contour line projection of the drain passage 41 in the axial direction of the flange 40 is located inside the inner circle of the cylinder liner 20, or when the contour line projection of the drain passage 41 in the axial direction of the flange 40 is located inside the inner circle of the cylinder liner 20, the contour line projection of the drain passage 41 in the axial direction of the flange 40 is located outside the contour line of the variable volume chamber 3111.

As shown in fig. 8, when the portion of the profile projection of the drain passage 41 in the axial direction of the flange 40 is located inside the inner circle of the cylinder liner 20, or when the profile projection of the drain passage 41 in the axial direction of the flange 40 is located inside the inner circle of the cylinder liner 20, the profile projection of the drain passage 41 in the axial direction of the flange 40 is located outside the profile of the shaft hole on the flange 40, and there is a first preset distance L between the drain passage 41 and the hole edge of the shaft hole.

In this embodiment, the ratio L/D2 between the first preset distance L and the hole diameter D2 of the shaft hole is >0.3.

As shown in fig. 22, the ratio of the height H2 of the connecting part between the two liquid discharge ports 22 in the axial direction of the cylinder liner 20 to the height H1 of the cylinder liner 20 in the axial direction thereof is in the range of 0.1 to 0.5.

As shown in fig. 22, the ratio of the depth H3 of the drain port 22 located above in the axial direction of the cylinder liner 20 to the height H1 of the cylinder liner 20 in the axial direction thereof is in the range of 0.1 to 0.4.

As shown in fig. 22, the ratio of the depth H4 of the drain port 22 located below in the axial direction of the cylinder liner 20 to the height H1 of the cylinder liner 20 in the axial direction thereof is in the range of 0.1 to 0.4.

As shown in fig. 23 to 25, the rotary shaft 10 is provided with two eccentric portions 11 along the axial direction thereof, the piston assembly 30 includes a piston sleeve 31 and a piston 32, wherein the piston sleeve 31 is rotatably disposed in the cylinder liner 20, the piston sleeve 31 has two limiting passages 311, the two limiting passages 311 are sequentially disposed along the axial direction of the rotary shaft 10, the extending direction of the limiting passages 311 is perpendicular to the axial direction of the rotary shaft 10, the piston 32 has a through hole, the two eccentric portions 11 correspondingly extend into the two through holes of the two pistons 32, the two pistons 32 correspondingly slide in the two limiting passages 311 and form a variable volume cavity 3111, the variable volume cavity 3111 is located in the sliding direction of the piston 32, and the rotary shaft 10 rotates to drive the piston 32 to slide reciprocally in the limiting passages 311 while interacting with the piston sleeve 31, so that the piston sleeve 31 and the piston 32 rotate in the cylinder liner 20.

As shown in fig. 22 and 24, the ratio of the height H2 of the connection between the two liquid discharge ports 22 in the axial direction of the cylinder liner 20 to the height H _q2 of the connection between the two limiting passages 311 in the axial direction of the piston sleeve 31 is in the range of 0.9 to 3.

As shown in fig. 22 and 25, the ratio of the height H2 of the connection between the two liquid discharge ports 22 in the axial direction of the cylinder liner 20 to the height H _q2 of the connection between the two stopper passages 311 in the axial direction of the piston sleeve 31 ranges from 1.1 to 1.2.

As shown in FIGS. 21 and 25, the width W1 of the liquid outlet 22 and the length L _qc of the channel wall of the limiting channel 311 satisfy that W1 is equal to or less than L _qc.

Preferably, the width W1 of the liquid outlet 22 and the length L _qc of the channel wall of the limiting channel 311 meet the condition that the value range of L _qc -W1 is 2-6 mm.

It should be noted that, in the present application, 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 channels 311 have a phase difference of a second angle B in the extending direction, wherein the first angle a is twice the second angle B.

Preferably, the two eccentric portions 11 are disposed 180 ° opposite each other.

Example two

The difference between this embodiment and the first embodiment is that, as shown in fig. 17 to 22, neither of the two liquid discharge ports 22 penetrates the outer peripheral surface of the cylinder liner 20.

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 utility model 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 refer to 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," "upper" and "upper surface," "above" and the like, may be used herein for ease of description to describe one device or feature's spatial relationship 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 process is carried out, the exemplary term "above" may be included. Upper and lower. Two orientations 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 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.

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

Claims (21)

1. A pump body assembly, comprising:

a rotating shaft (10);

the rotary shaft (10) and the cylinder sleeve (20) are eccentrically arranged, 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 disposed within the cylinder liner (20), and the spindle (10) being drivingly connected to the piston assembly (30) to vary the volume of the variable volume chamber (3111);

A liquid suction port (21) and a liquid discharge port (22) are arranged on the cylinder sleeve (20), the liquid suction port (21) is communicated with the variable-volume cavity (3111) and conveys a refrigerant into the variable-volume cavity (3111), and the liquid discharge port (22) is communicated with the variable-volume cavity (3111) and discharges the refrigerant in the variable-volume cavity (3111) from the liquid discharge port (22);

The two flanges (40) are respectively arranged at two axial ends of the cylinder sleeve (20);

The number of the liquid discharge ports (22) is two, and the two liquid discharge ports (22) are arranged at intervals along the axial direction of the cylinder sleeve (20);

At least one liquid outlet (22) of the two liquid outlets (22) penetrates through the axial end face of the cylinder sleeve (20), a liquid outlet channel (41) is formed in a flange (40) at least located on one side of the liquid outlet (22) penetrating through the axial end face of the cylinder sleeve (20), and the liquid outlet channel (41) is used for being communicated with the liquid outlet (22) on the same side.

2. Pump body assembly according to claim 1, characterized in that the drain channel (41) extends in the axial direction of the flange (40).

3. The pump body assembly of claim 1, wherein,

At least one liquid outlet (22) of the two liquid outlets (22) penetrates through the outer peripheral surface of the cylinder sleeve (20), or,

At least one liquid outlet (22) of the two liquid outlets (22) does not penetrate through the outer peripheral surface of the cylinder sleeve (20).

4. Pump body assembly according to claim 1, characterized in that the projection of the contour line of the drain channel (41) in the axial direction of the flange (40) is one of circular, rectangular, arc-shaped, profiled.

5. Pump body assembly according to claim 1, characterized in that the projection of the contour line of the drain channel (41) in the axial direction of the flange (40) is circular, and that D1 is smaller than or equal to W1 between the channel diameter D1 of the drain channel (41) and the width W1 of the drain port (22).

6. The pump body assembly of claim 1, wherein,

The projection of the contour line of the liquid discharge channel (41) on the axial direction of the flange (40) is positioned outside the inner circle of the cylinder sleeve (20), or,

The part of the drain channel (41) projected on the axial contour line of the flange (40) is positioned inside the inner circle of the cylinder sleeve (20), the other part of the drain channel (41) projected on the axial contour line of the flange (40) is positioned outside the inner circle of the cylinder sleeve (20), or,

A projection of a contour line of the liquid discharge channel (41) in the axial direction of the flange (40) is positioned in the inner circle of the cylinder sleeve (20).

7. Pump body assembly according to claim 1, characterized in that the contour projection of the drain channel (41) in the axial direction of the flange (40) is located outside the contour of the variable volume chamber (3111) when the portion of the contour projection of the drain channel (41) in the axial direction of the flange (40) is located inside the inner circle of the cylinder liner (20) or when the contour projection of the drain channel (41) in the axial direction of the flange (40) is located inside the inner circle of the cylinder liner (20).

8. Pump body assembly according to claim 1, characterized in that the contour projection of the drain channel (41) in the axial direction of the flange (40) is located outside the contour of the shaft hole on the flange (40) when the part of the contour projection of the drain channel (41) in the axial direction of the flange (40) is located within the inner circle of the cylinder sleeve (20) or when the contour projection of the drain channel (41) in the axial direction of the flange (40) is located within the inner circle of the cylinder sleeve (20), and that the drain channel (41) and the hole edge of the shaft hole have a first preset distance L between.

9. The pump body assembly of claim 8, wherein a ratio L/D2 between the first preset distance L and a bore diameter D2 of the shaft bore is >0.3.

10. Pump body assembly according to claim 1, characterized in that the ratio of the height H2 of the connection between the two liquid discharge ports (22) in the axial direction of the cylinder liner (20) to the height H1 of the cylinder liner (20) in the axial direction thereof is in the range of 0.1-0.5.

11. Pump body assembly according to claim 1, characterized in that the ratio of the depth H3 of the drain port (22) located above in the axial direction of the cylinder liner (20) to the height H1 of the cylinder liner (20) in the axial direction thereof is in the range of 0.1-0.4.

12. Pump body assembly according to claim 1, characterized in that the ratio of the depth H4 of the drain port (22) located below in the axial direction of the cylinder liner (20) to the height H1 of the cylinder liner (20) in the axial direction thereof is in the range of 0.1-0.4.

13. Pump body assembly according to any one of claims 1 to 12, wherein the rotary shaft (10) is provided with two eccentric portions (11) along its axial direction, the piston assembly (30) comprising:

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 the through-hole, piston (32) are two, two eccentric part (11) correspond to stretch into two in the through-hole of two piston (32), two piston (32) correspond the slip setting in two spacing passageway (311) and form become volume chamber (3111), become volume chamber (3111) and be located the slip direction of piston (32), 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. Pump body assembly according to claim 13, characterized in that the ratio of the height H2 of the connection between the two liquid discharge ports (22) in the axial direction of the cylinder sleeve (20) to the height H _q2 of the connection between the two limiting channels (311) in the axial direction of the piston sleeve (31) ranges from 0.9 to 3.

15. Pump body assembly according to claim 14, characterized in that the ratio of the height H2 of the connection between the two liquid discharge ports (22) in the axial direction of the cylinder sleeve (20) to the height H _q2 of the connection between the two limiting channels (311) in the axial direction of the piston sleeve (31) ranges from 1.1 to 1.2.

16. The pump body assembly according to claim 13, wherein the width W1 of the liquid outlet (22) and the length L _qc of the channel wall of the limiting channel (311) satisfy W1 is less than or equal to L _qc.

17. The pump body assembly according to claim 13, wherein the width W1 of the liquid outlet (22) and the length L _qc of the channel wall of the limiting channel (311) satisfy that the range of values of L _qc -W1 is 2-6 mm.

18. Pump body assembly according to claim 13, characterized in that the two eccentric parts (11) have a phase difference of a first angle a, the eccentric amounts of the two eccentric parts (11) are equal, and the two limiting channels (311) have a phase difference of a second angle B in the extending direction, wherein the first angle a is twice the second angle B.

19. Pump body assembly according to claim 18, characterized in that the two eccentric portions (11) are arranged 180 ° opposite each other.

20. A rotary cylinder pump comprising a pump body assembly as claimed in any one of claims 1 to 19.

21. A heat exchange apparatus comprising a rotary cylinder pump as claimed in claim 20.