WO2021098312A1

WO2021098312A1 - Pump body assembly, fluid machine, and heat exchange apparatus

Info

Publication number: WO2021098312A1
Application number: PCT/CN2020/110556
Authority: WO
Inventors: 胡余生; 魏会军; 徐嘉; 杜忠诚; 杨森; 任丽萍; 李直; 张培林; 张荣婷; 梁社兵; 丁宁; 史正良
Original assignee: 珠海格力电器股份有限公司
Priority date: 2019-11-22
Filing date: 2020-08-21
Publication date: 2021-05-27
Also published as: CN110905808A

Abstract

Disclosed are a pump body assembly, a fluid machine, and a heat exchange apparatus. The pump body assembly comprises: a piston (1); a rotary shaft (2); a cylinder (4) with an intake port (43) and an exhaust port (41); and a piston sleeve (3) located in the cylinder (4). The rotary shaft (2) drives the piston (1) to rotate and reciprocate in the piston sleeve (3) at the same time; a compression cavity (5) is formed between the piston (1) and the inner wall face of the air cylinder (4); and the compression cavity (5) is configured, when the pump assembly finishes exhausting and starts sucking in air, to be disengaged from the exhaust port (41) and rotate by an angle β, wherein the angle β is larger than 0° and smaller than or equal to 10°.

Description

Pump body components, fluid machinery and heat exchange equipment

Cross-references to related applications

The present disclosure is based on the application with the CN application number 201911158482.2 and the filing date on November 22, 2019, and claims its priority. The disclosure of the CN application is hereby incorporated into the present disclosure as a whole.

Technical field

The present disclosure relates to the field of heat exchange systems, and in particular to a pump body assembly, fluid machinery and heat exchange equipment.

Background technique

Rotary-cylinder piston compressor is a new type of positive displacement compressor. Its cylinder and shaft rotate around their respective centers, and the piston reciprocates relative to the cylinder and shaft at the same time. The reciprocating movement of the piston relative to the cylinder realizes the periodic enlargement and reduction of the volume cavity. The circular movement of the cylinder relative to the cylinder liner realizes that the compression chamber is connected to the suction port and the exhaust port respectively. The above two compound movements realize the compressor's suction, compression and discharge processes. The opening angle of the exhaust port of the rotary piston compressor is a key parameter, which has a significant impact on the performance.

Summary of the invention

According to one aspect of the present disclosure, there is provided a pump body assembly, including: a piston; a rotating shaft; a cylinder having an intake port and an exhaust port; a piston sleeve located in the cylinder, wherein the rotating shaft drives the piston While rotating, it reciprocates in the piston sleeve, and a compression chamber is formed between the piston and the inner wall surface of the cylinder. The compression chamber is configured to be configured to exhaust when the pump body assembly is exhausted and starts to inhale. It has departed from the exhaust port and rotated through an angle β, the angle β being greater than 0° and less than or equal to 10°.

In some embodiments, the angle β is between 4° and 6°.

In some embodiments, the piston has a set of opposed sliding surfaces, the sliding surface is matched with the piston sleeve, the distance between the set of sliding surfaces is B, and the radius of the inner circle of the cylinder is R; The center is the center of the circle, and the central angle M of the edge ends of the exhaust port and the suction port close to each other is equal to (2α+β), where α=arcsin(B/2R).

In some embodiments, the cylinder further has a pressure relief port, and the compression chamber is configured to communicate with the pressure relief port after exhausting.

In some embodiments, along the rotation direction of the piston, the pressure relief port is opened between the suction port and the exhaust port, and is close to the exhaust port.

In some embodiments, the piston has a set of opposed sliding surfaces, the sliding surface is matched with the piston sleeve, the distance between the set of sliding surfaces is B, and the radius of the inner circle of the cylinder is R; The center is the center of the circle, and the central angle Q between the edge ends of the pressure relief port and the suction port close to each other is greater than or equal to 1.25α and less than or equal to 1.5α, where α=arcsin(B/2R).

In some embodiments, the intake port includes: an intake passage communicated with the outside; an intake buffer groove communicated with the intake passage and opened on the inner wall of the cylinder, wherein the central angle M is the intake buffer groove close to the row The central angle between the edge on one side of the air port and the exhaust port. The central angle Q is the central angle between the edge of the inlet buffer groove near the pressure relief port and the pressure relief port.

In some embodiments, the intake buffer groove is symmetrically arranged with respect to the first reference plane, the first reference plane passes through the axis of the cylinder, the second reference plane is perpendicular to the first reference plane and passes through the axis of the cylinder, and the exhaust port is connected to the second reference plane. The central angle N between the reference planes is equal to (α+β), and the included angle γ between the pressure relief port and the second reference plane is greater than or equal to 0.25α and less than or equal to 0.5α.

In some embodiments, a compression cavity is formed between the extrusion surface of the piston and the inner wall surface of the cylinder, and one side edge of the extrusion surface is configured to be the same as the side edge of the intake buffer groove when the exhaust of the pump body assembly is completed. Coincident, the extrusion surface is a curved surface and the central angle of the curved surface is equal to 2α.

In some embodiments, the cylinder further has a pressure relief port, the compression chamber is configured to communicate with the pressure relief port after exhaust, and the ratio of the area of the pressure relief port to the area of the exhaust port is between 0.2 and 0.5.

According to another aspect of the present disclosure, there is provided a fluid machine including the above-mentioned pump body assembly.

In some embodiments, the fluid machine is a compressor.

According to another aspect of the present disclosure, there is provided a heat exchange device including the above-mentioned fluid machine.

Description of the drawings

The accompanying drawings of the specification constituting a part of the present disclosure are used to provide a further understanding of the present disclosure. The exemplary embodiments and descriptions of the present disclosure are used to explain the present disclosure, and do not constitute an improper limitation of the present disclosure. In the attached picture:

Fig. 1 shows a schematic diagram of the internal structure of a pump body assembly according to some embodiments of the present disclosure;

Figure 2 shows a schematic diagram of the position of the exhaust opening in Figure 1;

Figure 3 shows an enlarged view of position A in Figure 2;

Figure 4 shows a schematic diagram of the internal structure of a pump body assembly according to some embodiments of the present disclosure;

FIG. 5 shows a schematic diagram of the structure of the cylinder in FIG. 4;

Figure 6 shows an enlarged view of the pressure relief port and the exhaust port in Figure 5;

Figure 7 shows the relationship between the power consumption of the compressor and the area of the pressure relief port in the embodiment of Figure 4;

Figure 8 shows the relationship between the cooling capacity of the compressor and the area of the pressure relief port in the embodiment of Figure 4;

Figure 9 shows the relationship between the overall efficiency of the compressor and the area of the pressure relief port in the embodiment of Figure 4;

Among them, the above drawings include the following reference signs:

1. Piston; 11. Sealing surface; 2. Rotary shaft; 3. Piston sleeve; 4. Cylinder; 41. Exhaust port; 42. Pressure relief port; 43. Suction port; 431. Suction channel; 432. Inlet Buffer groove; 5. Compression cavity; 6. The first reference plane; 7. The second reference plane.

Detailed ways

It should be noted that the embodiments in the present disclosure and the features in the embodiments can be combined with each other if there is no conflict. Hereinafter, the present disclosure will be described in detail with reference to the drawings and in conjunction with the embodiments.

It should be noted that, unless otherwise specified, all technical and scientific terms used in the present disclosure have the same meaning as commonly understood by those of ordinary skill in the technical field to which the present disclosure belongs.

In the present disclosure, if there is no explanation to the contrary, the orientation words used such as "up, down, top, bottom" are usually directed to the direction shown in the drawings, or refer to the vertical, In terms of vertical or gravitational direction; similarly, for ease of understanding and description, "inner and outer" refers to the inner and outer relative to the contour of each component itself, but the above-mentioned directional words are not used to limit the present disclosure.

It is found through research that in the rotary piston compressor known to the inventor, when the pump body assembly is exhausted and starts to suck in, the exhaust port will communicate with the intake port, so that the exhaust port gas leaks into the piston head The suction port affects the performance of the whole machine.

In view of this, the present disclosure provides a pump body assembly, a fluid machine, and a heat exchange device, which can overcome the problem that the exhaust port gas leaks into the intake port through the piston head and affects the performance of the whole machine. Specifically, the fluid machine includes the following pump body components, the fluid machine is a compressor, and the heat exchange equipment includes the above-mentioned fluid machine or compressor.

As shown in FIGS. 1 to 3, in some embodiments, the pump body assembly includes a piston 1, a rotating shaft 2, a piston sleeve 3, and a cylinder 4. The rotating shaft 2 drives the piston 1 to rotate while reciprocating in the piston sleeve 3. The piston sleeve 3 is located in the cylinder 4, and the cylinder 4 has an intake port 43 and an exhaust port 41. A compression chamber 5 is formed between the inner wall surface of the piston 1 and the cylinder 4. When the pump body assembly is exhausted and begins to suck in, the compression chamber 5 has separated from the exhaust port 41 and rotated through an angle β, which is greater than 0° and less than or equal to 10°.

When the exhaust of the pump body assembly is completed and the suction starts, the compression chamber 5 and the exhaust port 41 have been separated, the exhaust port 41 and the head of the piston 1 have a sealing surface 11 within the β angle range, and the gas in the exhaust port 41 It will not leak into the suction port 43 through the head of the piston 1, which improves the performance of the whole machine.

As shown in Figures 2 and 3, in some embodiments, the angle β is between 4° and 6°. When the exhaust of the pump body assembly is completed and the suction starts, there is a sealing surface within the β angle range between the exhaust port 41 and the head gap of the piston 1, which is beneficial to prevent the high-pressure refrigerant in the exhaust port 41 from entering the suction through the head gap of the piston 1.气口43。 Air port 43. Among them, the performance is best when 4°<β<6°.

As shown in FIGS. 2 and 3, the piston 1 has a set of sliding surfaces arranged oppositely, and the sliding surfaces are matched with the piston sleeve 3. The distance between a set of sliding surfaces is B, and the radius of the inner circle of the cylinder 4 is R. Taking the center of the cylinder 4 as the center, the central angle M of the edge ends of the exhaust port 41 and the intake port 43 close to each other is equal to 2α+β, where α=arcsin(B/2R). In this embodiment, at the end of the exhaust, the exhaust port 41 is filled with high-pressure gas, and the intake port 43 is filled with low-pressure gas. At this time, the compression chamber 5 is also immediately connected with the suction port 43, and the central angle M of the edge ends of the exhaust port 41 and the suction port 43 close to each other is equal to (2α+β), so that the exhaust port 41 and the piston 1 head There is a sealing surface 11 in the β angle range between the gaps of the parts, which prevents the gas in the exhaust port 41 from entering the intake port 43 and improves the performance of the pump body assembly.

As shown in FIGS. 1 to 3, in some embodiments, the intake port 43 includes an intake passage 431 connected to the outside and an intake buffer groove 432 connected to the intake passage 431 and opened on the inner wall surface of the cylinder 4. . The central angle M is the central angle between the edge of the intake buffer groove 432 close to the exhaust port 41 and the exhaust port 41.

In this embodiment, in order to reduce the pressure of gas entering the cylinder 4, an intake buffer groove 432 is opened on the inner wall of the cylinder 4, and the intake buffer groove 432 communicates with the intake passage 431. When the pump body assembly is exhausted and starts to inhale, in order to ensure that the exhaust port 41 and the head of the piston 1 have a sealing surface 11 within the β angle range, the central angle M at this time is that the intake buffer groove 432 is close to the exhaust port 41 The central angle between the edge on one side and the exhaust port 41.

As shown in FIGS. 1 to 3, in some embodiments, the intake buffer groove 432 is symmetrically arranged with respect to the first reference plane 6, the first reference plane 6 passes through the axis of the cylinder 4, and the second reference plane 7 is perpendicular to the first reference plane 6. Refer to the plane 6 and pass through the axis of the cylinder 4. The central angle N between the exhaust port 41 and the second reference plane 7 is equal to (α+β), and the included angle γ between the pressure relief port 42 and the second reference plane 7 is greater than or equal to 0.25α and less than or equal to 0.5α.

In this embodiment, as shown in FIGS. 1 to 3, the intake buffer groove 432 has a symmetrical structure, and the projection of the first reference plane 6 along the plane perpendicular to the cylinder 4 corresponds to the vertical line passing through the center of the cylinder 4 in FIGS. 1 to 3 , The second reference plane 7 corresponds to the horizontal line passing through the center of the cylinder 4 in Figs. 1 to 3, which can be deduced as α=arcsin(B/2R), and the angle β corresponds to the sealing surface 11 of the exhaust port 41, between γ and α The relationship between γ is greater than or equal to 0.25α and less than or equal to 0.5α.

As shown in Figures 1 to 3, a compression chamber 5 is formed between the extrusion surface of the piston 1 and the inner wall surface of the cylinder 4. When the exhaust of the pump body assembly is completed, one side edge of the extrusion surface and the intake buffer groove 432 One side of the edge coincides, the extrusion surface is a curved surface and the central angle of the curved surface is equal to 2α. In this embodiment, the piston 1 has a set of oppositely arranged sliding surfaces, the sliding surfaces are matched with the piston sleeve 3, the distance between the sliding surfaces is B, and the radius of the inner circle of the cylinder 4 is R, α The angle of is equal to arcsin(B/2R), so the extrusion surface is arc and the central angle of arc is equal to 2α.

In some embodiments, the cylinder 4 is provided with a pressure relief port 42 in addition to an intake port 43 and an exhaust port 41.

As shown in FIGS. 4 to 6, the cylinder 4 also has a pressure relief port 42, and the compression chamber 5 can communicate with the pressure relief port 42 after exhausting. In the late exhaust stage, the gap between the head of the piston 1 and the cylinder gradually decreases. At this time, the gas exhaust resistance in the area farther from the exhaust port 41 in the compression chamber 5 is relatively large, and the overcompression is serious, which affects the performance of the pump body assembly. A pressure relief port 42 is provided on the cylinder 4. The pressure relief port 42 can communicate with the compression chamber 5 after exhausting, so as to discharge the residual refrigerant in the compression chamber 5. This not only improves the efficiency of the pump assembly, but also reduces the number of pumps. The pressure on the parts in the body assembly reduces vibration and improves the stability of the pump body assembly.

As shown in Figures 4 to 6, in some embodiments, the cylinder 4 also has a pressure relief port 42. Along the rotation direction of the piston 1, the pressure relief port 42 is opened between the suction port 43 and the exhaust port 41, and Close to the exhaust port 41. The pressure relief port 42 is arranged between the suction port 43 and the exhaust port 41 along the rotation direction of the piston 1 to ensure that the compression chamber 5 passes through the pressure relief port 42 after exhausting, so as to discharge residual refrigerant. The pressure relief port 42 is opened close to the exhaust port 41, which is beneficial to reduce the gas pressure around the exhaust port 41 and prevent over-compression.

As shown in Figures 4 to 6, in some embodiments, the piston 1 has a set of opposed sliding surfaces, the sliding surfaces are matched with the piston sleeve 3, and the distance between the set of sliding surfaces is B, and the cylinder The radius of the inner circle of 4 is R; taking the center of the cylinder 4 as the center, the central angle Q of the edge ends of the pressure relief port 42 and the suction port 43 close to each other is greater than or equal to 1.25α and less than or equal to 1.5α, where α= arcsin(B/2R). At the end of the exhaust, the compression chamber 5 continues to rotate and starts to inhale. At this time, the suction port 43 will communicate with the pressure relief port 42. When the central angle M is greater, the arc between the pressure relief port 42 and the suction port 43 The greater the length, when the compression chamber 5 rotates through the pressure relief port 42, the high-pressure gas in the compression chamber 5 will leak into the suction port 43, which will increase the leakage of the pump body assembly and reduce the performance. Therefore, it is necessary to adjust the angle Q Make restrictions.

As shown in FIGS. 4 to 6, the central angle Q is the central angle between the edge of the intake buffer groove 432 on the side close to the pressure relief port 42 and the pressure relief port 42. In this embodiment, in order to reduce the pressure of gas entering the cylinder 4, an intake buffer groove 432 is opened on the inner wall of the cylinder 4. The intake buffer groove 432 is connected to the intake passage 431, and the angle Q is also restricted. The edge of the air buffer groove 432 shall prevail.

As shown in FIGS. 4 to 6, in some embodiments, the included angle γ between the pressure relief port 42 and the second reference plane 7 is greater than or equal to 0.25α and less than or equal to 0.5α. In this embodiment, as shown in Figs. 4 to 6, the air intake buffer groove 432 has a symmetrical structure. The projection of the first reference plane 6 along the plane perpendicular to the cylinder 4 corresponds to the vertical line passing through the center of the cylinder 4 in FIGS. 4 to 6, and the second reference plane 7 corresponds to the horizontal line passing through the center of the cylinder 4 in FIGS. 1 to 5, which can be pushed Obtain α=arcsin(B/2R), the angle β corresponds to the sealing distance of the exhaust port 41, and the relationship between γ and α is that γ is greater than or equal to 0.25α and less than or equal to 0.5α.

As shown in FIGS. 6 to 9, the compression chamber 5 can communicate with the pressure relief port 42 after exhaust, and the ratio of the area of the pressure relief port 42 to the area of the exhaust port 41 is between 0.2 and 0.5. The diameter of the pressure relief port is defined as d, and the area is S2=πd ² /4; the diameter of the exhaust port is D, and the area is respectively S1=πD ² /4. The smaller the area of the pressure relief port 42 is, the smaller the area of the pressure relief channel will increase the exhaust resistance, which will affect the pressure relief capability and increase the power consumption. If the area of the pressure relief port 42 is too large, the clearance volume of the compressor will increase. It will also cause an increase in power consumption and a decrease in performance. The specific relationship is shown in Figure 7 to Figure 9. The area of the pressure relief port 42 needs to be within an appropriate range. When the ratio between S2 and S1 is between 0.2 and 0.5, the performance of the pump body assembly is optimal, and thus the performance of the compressor is optimal.

The pump body assembly also includes an upper flange, a lower flange, an upper limit plate, and a lower limit plate. The piston sleeve 3 and the rotating shaft 2 rotate around their respective centers, and the piston 1 reciprocates relative to the piston sleeve 3 and the rotating shaft 2 at the same time. The reciprocating movement of the piston 1 relative to the piston sleeve 3 realizes the periodical enlargement and reduction of the compression chamber 5. The piston sleeve 3 moves in a circular motion relative to the cylinder 4 to realize the communication of the compression chamber 5 with the suction port 43 and the discharge port 41 respectively; the above two combined movements realize the suction, compression, and discharge processes of the pump body group.

In the above-mentioned embodiment of the present disclosure, the piston sleeve is located in the cylinder. The cylinder has an intake port and an exhaust port. A compression chamber is formed between the piston and the inner wall surface of the cylinder. When the exhaust of the pump body assembly is completed and the intake is started, the compression chamber It has been separated from the exhaust port and rotated through β, which is greater than 0° and less than or equal to 10°. When the pump body components are exhausted and start to inhale, the compression chamber and the exhaust port have been separated, the exhaust port and the piston head have a sealing surface within the β angle range, and the gas in the exhaust port will not leak through the piston head Enter the suction port to improve the performance of the whole machine.

Obviously, the embodiments described above are only a part of the embodiments of the present disclosure, rather than all the embodiments. Based on the embodiments in the present disclosure, all other embodiments obtained by those of ordinary skill in the art without creative work should fall within the protection scope of the present disclosure.

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

It should be noted that the terms “first”, “second”, etc. in the specification and claims of the present disclosure and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific sequence or sequence. It should be understood that the data used in this way can be interchanged under appropriate circumstances so that the embodiments of the present disclosure described herein can be implemented in an order other than those illustrated or described herein.

The above are only preferred embodiments of the present disclosure, and are not used to limit the present disclosure. For those skilled in the art, the present disclosure may have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present disclosure shall be included in the protection scope of the present disclosure.

Claims

A pump body assembly including:

Piston (1);

Shaft (2);

The cylinder (4) has an intake port (43) and an exhaust port (41);

The piston sleeve (3) is located in the cylinder (4),

Wherein, the rotating shaft (2) drives the piston (1) to rotate while reciprocating in the piston sleeve (3), and compression is formed between the piston (1) and the inner wall surface of the cylinder (4). The cavity (5), the compression cavity (5) is configured to have separated from the exhaust port (41) and rotated through an angle β when the pump body assembly is exhausted and starts to inhale. Greater than 0° and less than or equal to 10°.
The pump body assembly according to claim 1, wherein the angle β is between 4° and 6°.
The pump body assembly according to claim 1, wherein the piston (1) has a set of sliding surfaces arranged oppositely, and the sliding surface is matched with the piston sleeve (3), and a set of the sliding surfaces is matched with the piston sleeve (3). The distance between the moving surfaces is B, and the radius of the inner circle of the cylinder (4) is R;

Taking the center of the cylinder (4) as the center of the circle, the central angle M of the edge ends of the exhaust port (41) and the suction port (43) that are close to each other is equal to (2α+β), where α= arcsin(B/2R).
The pump body assembly according to claim 1, wherein the cylinder (4) further has a pressure relief port (42), and the compression chamber (5) is configured to communicate with the pressure relief port (42) after exhausting. ) Connected.
The pump body assembly according to claim 4, wherein, along the rotation direction of the piston (1), the pressure relief port (42) is opened in the suction port (43) and the exhaust port (41). ) And close to the exhaust port (41).
The pump body assembly according to claim 5, wherein the piston (1) has a set of sliding surfaces arranged oppositely, and the sliding surface is matched with the piston sleeve (3), and a set of the sliding surfaces is matched with the piston sleeve (3). The distance between the moving surfaces is B, and the radius of the inner circle of the cylinder (4) is R;

Taking the center of the cylinder (4) as the center of the circle, the central angle Q of the edge ends of the pressure relief port (42) and the suction port (43) that are close to each other is greater than or equal to 1.25α and less than or equal to 1.5α, Where α=arcsin(B/2R).
The pump body assembly according to claim 3 or 6, wherein the suction port (43) comprises:

The suction channel (431) connected to the outside;

An intake buffer groove (432) connected to the intake passage (431) and opened on the inner wall surface of the cylinder (4),

Wherein, the central angle M is the central angle between the edge of the intake buffer groove (432) close to the exhaust port (41) and the exhaust port (41), and the central angle Q is The central angle between the edge of the air inlet buffer groove (432) close to the pressure relief port (42) and the pressure relief port (42).
The pump body assembly according to claim 7, wherein the intake buffer groove (432) is symmetrically arranged with respect to a first reference plane (6), and the first reference plane (6) passes through the cylinder (4) The second reference plane (7) is perpendicular to the first reference plane (6) and passes through the axis of the cylinder (4), and the exhaust port (41) is connected to the second reference plane (7) The central angle N between them is equal to (α+β), and the included angle γ between the pressure relief port (42) and the second reference plane (7) is greater than or equal to 0.25α and less than or equal to 0.5α.
The pump body assembly according to claim 7, wherein a compression cavity (5) is formed between the extrusion surface of the piston (1) and the inner wall surface of the cylinder (4), and one side of the extrusion surface The edge is configured to coincide with one side edge of the intake buffer groove (432) when the pump body assembly is exhausted, the extrusion surface is a curved surface and the central angle of the curved surface is equal to 2α.
The pump body assembly according to claim 1, wherein the cylinder (4) further has a pressure relief port (42), and the compression chamber (5) is configured to communicate with the pressure relief port (42) after exhausting. ) Is connected, and the ratio of the area of the pressure relief port (42) to the area of the exhaust port (41) is between 0.2 and 0.5.
A fluid machine, comprising the pump body assembly according to any one of claims 1 to 10.
The fluid machine according to claim 11, wherein the fluid machine is a compressor.
A heat exchange device comprising the fluid machine according to claim 11 or 12.