Pump body assembly, fluid machinery and heat exchange equipment

Abstract

The present invention provides a pump body assembly, a fluid machine and a heat exchange device. The pump body assembly includes: a piston; a rotating shaft; a piston sleeve, the rotating shaft drives the piston to rotate and reciprocate within the piston sleeve; a cylinder, the piston sleeve is located within the cylinder, the cylinder has an air inlet and an air outlet, a compression chamber is formed between the piston and the inner wall surface of the cylinder. When the pump body assembly finishes exhausting and starts to inhale, the compression chamber has disengaged from the air outlet and rotated through an angle β, where β is greater than 0° and less than or equal to 10°. The present invention solves the problem in the prior art that the gas at the air outlet leaks into the air inlet through the piston head, affecting the performance of the whole machine.

Description

Technical Field

[0001] The present invention relates to the field of heat exchange systems, and in particular, to a pump body assembly, a fluid machine, and a heat exchange device. Background Art

[0002] A rotating cylinder piston compressor is a new type of positive displacement compressor. Its cylinder and rotating shaft rotate around their respective centers, and the piston reciprocates relative to both the cylinder and the rotating shaft. The reciprocating motion of the piston relative to the cylinder realizes the periodic expansion and contraction of the volume chamber. The circumferential motion of the cylinder relative to the cylinder liner realizes the communication of the compression chamber with the suction port and the discharge port respectively. The above two combined motions realize the suction, compression, and discharge processes of the compressor. The opening angle of the discharge port of the rotating cylinder piston compressor is a key parameter and has a significant impact on the performance.

[0003] In the prior art, when the pump body assembly finishes discharging and starts to suck in air, the discharge port will communicate with the suction port, causing the gas at the discharge port to leak into the suction port through the piston head, affecting the performance of the whole machine. Summary of the Invention

[0004] The main object of the present invention is to provide a scroll compressor to solve the problem in the prior art that the gas at the discharge port leaks into the suction port through the piston head, affecting the performance of the whole machine.

[0005] To achieve the above object, according to one aspect of the present invention, there is provided a pump body assembly, including: a piston; a rotating shaft; a piston sleeve, the rotating shaft drives the piston to rotate while reciprocating in the piston sleeve; a cylinder, the piston sleeve is located in the cylinder, the cylinder has a suction port and a discharge port, a compression chamber is formed between the piston and the inner wall surface of the cylinder, when the pump body assembly finishes discharging and starts to suck in air, the compression chamber has separated from the discharge port and rotated by β, where β is greater than 0° and less than or equal to 10°.

[0006] Further, β is between 4° and 6°.

[0007] Further, the piston has a set of oppositely arranged sliding surfaces, the sliding surfaces cooperate with the piston sleeve, the distance between the set of sliding surfaces is B, and the radius of the inner diameter of the cylinder is R; with the center of the cylinder as the center of the circle, the central angle M opposite to the edge ends where the discharge port and the suction port are close to each other is equal to (2α + β), where α = arcsin(B / 2R).

[0008] Further, the cylinder further has a pressure relief port, and the compression chamber can communicate with the pressure relief port after discharging.

[0009] Further, the cylinder further has a pressure relief port, along the rotation direction of the piston, the pressure relief port is opened between the suction port and the discharge port and is close to the discharge port.

[0010] Further, the piston has a set of relatively arranged sliding surfaces, which cooperate with the piston sleeve. The distance between the set of sliding surfaces is B, and the radius of the inner diameter of the cylinder is R. With the center of the cylinder as the center of the circle, the central angle Q formed by the edges of the pressure relief port and the suction port 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).

[0011] Further, the suction port includes: a suction channel communicating with the outside; an intake buffer groove communicating with the suction channel and opened on the inner wall surface of the cylinder. The central angle M is the central angle formed by the edge of the intake buffer groove close to the exhaust port and the exhaust port, and the central angle Q is the central angle formed by the edge of the intake buffer groove close to the pressure relief port and the pressure relief port.

[0012] Further, the intake buffer groove is symmetrically arranged with respect to the first reference plane. The first reference plane passes through the radial direction of the cylinder. The second reference plane is perpendicular to the first reference plane and passes through the radial direction of the cylinder. The central angle N between the exhaust port and the second reference plane 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.

[0013] Further, a compression chamber is formed between the extrusion surface of the piston and the inner wall surface of the cylinder. When the exhaust of the pump body assembly is completed, one edge of the extrusion surface coincides with one edge of the intake buffer groove. The extrusion surface is an arc surface and the central angle of the arc surface is equal to 2α.

[0014] Further, the cylinder also has a pressure relief port. The compression chamber can communicate with the pressure relief port after exhaust. The ratio of the area of the pressure relief port to the area of the exhaust port is between 0.2 and 0.5.

[0015] According to another aspect of the present invention, a fluid machine is provided, including the above-mentioned pump body assembly.

[0016] Further, the fluid machine is a compressor.

[0017] According to another aspect of the present invention, a heat exchange device is provided, including the above-mentioned fluid machine.

[0018] Applying the technical solution of the present invention, the piston sleeve is located inside the cylinder. The cylinder has a suction 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 starts to inhale, the compression chamber has separated from the exhaust port and rotated through β, where β is greater than 0° and less than or equal to 10°. When the exhaust of the pump body assembly is completed and starts to inhale, the compression chamber has separated from the exhaust port. There is a sealing surface within the β angle range between the exhaust port and the piston head. The gas in the exhaust port will not leak into the suction port through the piston head, improving the overall performance of the machine. Description of the Drawings

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

[0020] Figure 1 shows a schematic internal structure diagram of a pump body assembly according to Embodiment 1 of the present invention; and

[0021] Figure 2 shows Figure 1 a schematic diagram of the position where an exhaust port is opened;

[0022] Figure 3 shows Figure 2 an enlarged view of position A;

[0023] Figure 4 shows a schematic internal structure diagram of a pump body assembly according to Embodiment 2 of the present invention;

[0024] Figure 5 shows Figure 4 a schematic diagram of the structure of a cylinder;

[0025] Figure 6 shows Figure 5 an enlarged view of a pressure relief port and an exhaust port;

[0026] Figure 7 shows a relationship diagram between the power consumption of a compressor in Embodiment 2 and the area of the pressure relief port;

[0027] Figure 8 shows a relationship diagram between the cooling capacity of a compressor in Embodiment 2 and the area of the pressure relief port;

[0028] Figure 9 shows a relationship diagram between the comprehensive efficiency of a compressor in Embodiment 2 and the area of the pressure relief port;

[0029] Among them, the above-mentioned drawings include the following reference numerals:

[0030] 1, piston; 11, sealing surface; 2, rotating shaft; 3, piston sleeve; 4, cylinder; 41, exhaust port; 42, pressure relief port; 43, suction port; 431, suction channel; 432, intake buffer groove; 5, compression chamber; 6, first reference plane; 7, second reference plane. Detailed Embodiments

[0031] It should be noted that, without conflict, the embodiments in this application and the features in the embodiments can be combined with each other. The present invention will be described in detail below with reference to the drawings and in conjunction with the embodiments.

[0032] It should be noted that, unless otherwise specified, all technical and scientific terms used in this application have the same meaning as commonly understood by those of ordinary skill in the technical field to which this application belongs.

[0033] In the present invention, in the absence of contrary description, the orientation terms such as "upper, lower, top, bottom" are generally in reference to the direction shown in the drawings, or in reference to the vertical, perpendicular or gravitational direction of the component itself; similarly, for the sake of easy understanding and description, "inner, outer" refer to the inner and outer of the contour of each component itself, but the above orientation terms are not used to limit the present invention.

[0034] To solve the problem that in the prior art, the gas at the exhaust port leaks into the suction port through the piston head, affecting the performance of the whole machine, the present invention provides a pump body assembly, a fluid machine and a heat exchange device. Specifically, the fluid machine includes the following pump body assembly, the fluid machine is a compressor, and the heat exchange device includes the above fluid machine or compressor.

[0035] Embodiment 1

[0036] As Figures 1 to 3 shown, the pump body assembly in the present invention includes a piston 1, a rotating shaft 2, a piston sleeve 3, and a cylinder 4. While the rotating shaft 2 drives the piston 1 to rotate, the piston 1 reciprocates within the piston sleeve 3. The piston sleeve 3 is located within the cylinder 4. The cylinder 4 has a suction port 43 and an exhaust port 41. A compression chamber 5 is formed between the piston 1 and the inner wall surface of the cylinder 4. When the pump body assembly finishes exhausting and starts to inhale, the compression chamber 5 has disengaged from the exhaust port 41 and rotated through an angle β, where β is greater than 0° and less than or equal to 10°.

[0037] The piston sleeve 3 is located within the cylinder 4. The cylinder 4 has a suction port 43 and an exhaust port 41. A compression chamber 5 is formed between the piston 1 and the inner wall surface of the cylinder 4. When the pump body assembly finishes exhausting and starts to inhale, the compression chamber 5 has disengaged from the exhaust port 41 and rotated through an angle β, where β is greater than 0° and less than or equal to 10°. When the pump body assembly finishes exhausting and starts to inhale, the compression chamber 5 and the exhaust port 41 have already disengaged. There is a sealing surface 11 within an angular range of β between the exhaust port 41 and the piston head. The gas within the exhaust port 41 will not leak into the suction port 43 through the piston head, improving the performance of the whole machine.

[0038] As Figure 2 and Figure 3 shown, β is between 4° and 6°. When the pump body assembly finishes exhausting and starts to inhale, there is a sealing surface within an angular range of β in the gap between the exhaust port 41 and the piston head, which is beneficial to preventing the high-pressure refrigerant within the exhaust port 41 from entering the suction port 43 through the gap of the piston head. Among them, the performance is optimal when 4° < β < 6°.

[0039] As Figure 2 and Figure 3As shown in the figure, the piston 1 has a set of relatively arranged sliding surfaces that cooperate with the piston sleeve 3. The distance between the set of sliding surfaces is B, and the radius of the inner diameter of the cylinder 4 is R. Taking the center of the cylinder 4 as the center of the circle, the central angle M corresponding to 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). In this embodiment, at the end of exhaust, the pressure in the exhaust port 41 is high-pressure gas, and the pressure in the suction port 43 is low-pressure gas. At this time, the compression chamber 5 is also immediately connected to the suction port 43, and the central angle M corresponding to the edge ends of the exhaust port 41 and the suction port 43 that are close to each other is equal to (2α + β), so that there is a sealing surface 11 within the range of the β angle between the exhaust port 41 and the gap of the piston 1 head, preventing the gas in the exhaust port 41 from entering the suction port 43 and improving the performance of the pump body assembly.

[0040] As Figures 1 to 3 shown, the suction port 43 includes a suction channel 431 communicating with the outside and an intake buffer groove 432 communicating with the suction channel 431 and opened on the inner wall surface of the cylinder 4. The central angle M is the central angle corresponding to the side edge of the intake buffer groove 432 close to the exhaust port 41 and the exhaust port 41.

[0041] In this embodiment, in order to slow down the pressure of the 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 suction channel 431. When the pump body assembly finishes exhausting and starts to inhale, in order to ensure that there is a sealing surface 11 within the range of the β angle between the exhaust port 41 and the piston 1 head, at this time, the central angle M is the central angle corresponding to the side edge of the intake buffer groove 432 close to the exhaust port 41 and the exhaust port 41.

[0042] As Figures 1 to 3 shown, the intake buffer groove 432 is symmetrically arranged with respect to the first reference plane 6. The first reference plane 6 passes through the radial direction of the cylinder 4. The second reference plane 7 is perpendicular to the first reference plane 6 and passes through the radial direction 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.

[0043] In this embodiment, as Figures 1 to 3 shown, the intake buffer groove 432 is a symmetric structure. The first reference plane 6 corresponds to Figures 1 to 3 the vertical line passing through the center of the cylinder 4 in the plane projection perpendicular to the cylinder 4, and the second reference plane 7 corresponds to Figures 1 to 3 the horizontal line passing through the center of the cylinder 4. It can be deduced that α = arcsin(B / 2R), the β angle corresponds to the sealing surface 11 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.

[0044] As Figures 1 to 3As shown, a compression chamber 5 is formed between the pressing 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 pressing surface coincides with one side edge of the intake buffer groove 432. The pressing surface is an arc surface and the central angle of the arc surface is equal to 2α. In this embodiment, the piston 1 has a set of oppositely arranged sliding surfaces that cooperate with the piston sleeve 3. The distance between the set of sliding surfaces is B, the radius of the inner diameter of the cylinder 4 is R, and the angle of α is equal to arcsin(B / 2R). Therefore, the pressing surface is an arc surface and the central angle of the arc surface is equal to 2α.

[0045] Embodiment 2

[0046] The difference from Embodiment 1 is that in addition to the intake port 43 and the exhaust port 41, the cylinder 4 is further provided with a pressure relief port 42.

[0047] As Figures 4 to 6 shown, the cylinder 4 is further provided with a pressure relief port 42, and the compression chamber 5 can communicate with the pressure relief port 42 after exhaust. In the later stage of exhaust, the space between the head of the piston 1 and the cylinder gradually decreases. At this time, the gas exhaust resistance in the area of the compression chamber 5 farther from the exhaust port 41 is large, and over-compression is serious, affecting the performance of the pump body assembly. By providing the pressure relief port 42 on the cylinder 4, the pressure relief port 42 can communicate with the compression chamber 5 after exhaust, so as to discharge the residual refrigerant in the compression chamber 5. This can not only improve the efficiency of the pump body assembly, but also reduce the pressure borne by the parts in the pump body assembly, reduce vibration, and improve the operating stability of the pump body assembly.

[0048] As Figures 4 to 6 shown, the cylinder 4 is further provided with a pressure relief port 42. Along the rotation direction of the piston 1, the pressure relief port 42 is opened between the intake port 43 and the exhaust port 41 and is close to the exhaust port 41. The pressure relief port 42 being arranged between the intake port 43 and the exhaust port 41 along the rotation direction of the piston 1 can ensure that the compression chamber 5 passes through the pressure relief port 42 after exhaust, so as to discharge the residual refrigerant. The pressure relief port 42 being opened close to the exhaust port 41 is beneficial to reducing the gas pressure around the exhaust port 41 and preventing over-compression.

[0049] As Figures 4 to 6As shown, the piston 1 has a set of sliding surfaces arranged opposite to each other, and the sliding surfaces match the piston sleeve 3. The distance between the sliding surfaces is B, and the radius of the inner diameter of the cylinder 4 is R. With 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 air intake 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). When the exhaust is finished, the compression chamber 5 continues to rotate and starts to inhale. At this time, the air intake port 43 will be connected with the pressure relief port 42. When the central angle M is larger, the arc length between the pressure relief port 42 and the air intake port 43 is larger. When the compression chamber 5 rotates past the pressure relief port 42, the high-pressure gas in the compression chamber 5 will leak into the air intake port 43, increasing the leakage of the pump body assembly and reducing the performance. Therefore, it is necessary to limit the angle Q.

[0050] like Figures 4 to 6 As shown, the central angle Q is the central angle between the edge of the air intake buffer groove 432 close to the pressure relief port 42 and the pressure relief port 42. In this embodiment, in order to reduce the pressure of the gas entering the cylinder 4, an air intake buffer groove 432 is opened on the inner wall of the cylinder 4, and the air intake buffer groove 432 is connected to the air intake channel 431. The angle Q limit also needs to be based on the edge of the air intake buffer groove 432.

[0051] like Figures 4 to 6 As shown, the 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. Figures 4 to 6 As shown, the intake buffer groove 432 is a symmetrical structure, and the first reference plane 6 is projected along a plane perpendicular to the cylinder 4 corresponding to Figures 4 to 6 The vertical line passing through the center of the cylinder 4, the second reference plane 7 corresponds to Figures 1 to 5 From the horizontal line passing through the center of the cylinder 4, it can be deduced that 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.

[0052] like Figures 6 to 9 As shown, the compression chamber 5 can be connected to 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 its area is S1=S1=πd 2 / 4. The smaller the area of ​​the pressure relief port 42, the smaller the area of ​​the pressure relief channel, the greater the exhaust resistance, which affects the pressure relief capacity and leads to increased power consumption. If the area of ​​the pressure relief port 42 is too large, the clearance volume of the compressor will become larger, which will also lead to increased power consumption and decreased performance. For the specific relationship, see the attached Figure 7 To Attachment Figure 9As shown. In summary, the area of the pressure relief port 42 needs to be within a suitable 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.

[0053] The pump body assembly further includes an upper flange, a lower flange, an upper limit plate, and a lower limit plate. Its piston sleeve 3 and the rotating shaft 2 rotate around their respective centers, and the piston 1 reciprocates simultaneously relative to the piston sleeve 3 and the rotating shaft 2. The reciprocating motion of the piston 1 relative to the piston sleeve 3 realizes the periodic expansion and contraction of the compression chamber 5. The piston sleeve 3 makes a circular motion relative to the cylinder 4, realizing the communication of the compression chamber 5 with the suction port 43 and the exhaust port 41 respectively; the above two combined motions realize the suction, compression, and exhaust processes of the pump body group.

[0054] Obviously, the above-described embodiments are only a part of the embodiments of the present invention, rather than all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without making creative efforts shall fall within the protection scope of the present invention.

[0055] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they specify the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0056] It should be noted that the terms "first", "second", etc. in the specification and claims of the present application and the above drawings are used to distinguish similar objects and do not necessarily need to describe a specific order or sequence. It should be understood that such used data can be interchanged under appropriate circumstances so that the embodiments of the present application described herein can be implemented in an order different from those illustrated or described herein.

[0057] The above are only the preferred embodiments of the present invention and are not used to limit the present invention. For those skilled in the art, the present invention can have various changes and modifications. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A pump body assembly, characterized in that, it includes: a piston (1); a rotating shaft (2); a piston sleeve (3), while the rotating shaft (2) drives the piston (1) to rotate, the piston (1) reciprocates within the piston sleeve (3); a cylinder (4), the piston sleeve (3) is located within the cylinder (4), the cylinder (4) has an air inlet (43) and an air outlet (41), a compression chamber (5) is formed between the piston (1) and the inner wall surface of the cylinder (4), when the exhaust of the pump body assembly is completed and the suction starts, the compression chamber (5) has disengaged from the air outlet (41) and rotated through an angle β, where β is greater than 0° and less than or equal to 10°.

2. The pump body assembly according to claim 1, characterized in that, β is between 4° and 6°.

3. The pump body assembly according to claim 1, characterized in that, the piston (1) has a set of oppositely arranged sliding surfaces, the sliding surfaces cooperate with the piston sleeve (3), the distance between a set of the sliding surfaces is B, and the radius of the inner diameter of the cylinder (4) is R; with the center of the cylinder (4) as the center of the circle, the central angle M formed by the edges of the air outlet (41) and the air inlet (43) that are close to each other is equal to (2α + β), where α = arcsin(B / 2R).

4. The pump body assembly according to claim 1, characterized in that, the cylinder (4) also has a pressure relief port (42), and the compression chamber (5) can communicate with the pressure relief port (42) after exhaust.

5. The pump body assembly according to claim 4, characterized in that, 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 air inlet (43) and the air outlet (41), and is close to the air outlet (41).

6. The pump body assembly according to claim 5, characterized in that, the piston (1) has a set of oppositely arranged sliding surfaces, the sliding surfaces cooperate with the piston sleeve (3), the distance between a set of the sliding surfaces is B, and the radius of the inner diameter of the cylinder (4) is R; with the center of the cylinder (4) as the center of the circle, the central angle Q formed by the edges of the pressure relief port (42) and the air inlet (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).

7. The pump body assembly according to claim 3 or 6, characterized in that, the air inlet (43) includes: an air suction channel (431) communicating with the outside; an air intake buffer groove (432) communicating with the air suction channel (431) and opened on the inner wall surface of the cylinder (4), the central angle M is the central angle formed between the edge of the air intake buffer groove (432) close to the air outlet (41) and the air outlet (41), and the central angle Q is the central angle formed between the edge of the air intake buffer groove (432) close to the pressure relief port (42) and the pressure relief port (42).

8. The pump body assembly according to claim 7, characterized in that, The intake buffer groove (432) is symmetrically arranged with respect to the first reference plane (6), the first reference plane (6) passes through the radial direction of the cylinder (4), the second reference plane (7) is perpendicular to the first reference plane (6) and passes through the radial direction 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 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.

9. The pump body assembly according to claim 7, characterized in that, 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 coincides with one side edge of the intake buffer groove (432), the extrusion surface is an arc surface and the central angle of the arc surface is equal to 2α.

10. The pump body assembly according to claim 1, characterized in that, the cylinder (4) further has a pressure relief port (42), 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.

11. A fluid machine, characterized in that, comprises the pump body assembly according to any one of claims 1 to 10.

12. The fluid machine according to claim 11, characterized in that, the fluid machine is a compressor.

13. A heat exchange device, characterized in that, comprises the fluid machine according to claim 11 or 12.

Images