Exhaust assembly for compressors, pump body assembly, compressors and air conditioners

Abstract

This invention provides a compressor exhaust assembly, a pump body assembly, a compressor, and an air conditioner. The compressor exhaust assembly includes an exhaust valve plate and a limiter. The exhaust valve plate covers the flange exhaust port, and the limiter is located on one side of the exhaust valve plate. The limiter includes a straight section and a curved section. The straight section has a mounting hole, and the curved section is cantilevered. The compressor's maximum operating frequency is f, the flange exhaust port diameter is d, the limiter thickness is T, the maximum lift of the curved section is H, the projected length of the curved section on the mounting plane of the straight section is L, the radius of curvature of the curved section is R0, the radian angle is β, and the exhaust volume of the working chamber is V. The parameters f, β, H, L, R0, and V satisfy: 0.8 ≤ f*V / [L*(H-R0)+β*R0] 2 The frequency is ≤27.6 and f≥120Hz. The compressor exhaust assembly according to the present invention can improve the high-frequency exhaust smoothness of the compressor, reduce exhaust flow resistance and airflow pulsation, thereby improving the high-frequency reliability of the valve plate and playing the role of improving efficiency and reducing noise.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more specifically, to a compressor exhaust assembly, a pump body assembly, a compressor, and an air conditioner. Background Technology

[0002] The rotary compressor pump assembly includes major components such as cylinders, crankshaft, rollers, upper and lower flanges, vanes, and exhaust components. These components work together to form a sealed intake and exhaust chamber. Driven by the rotation of the crankshaft, the volume of the compressor's intake and exhaust chambers changes, thus realizing the compressor's periodic intake, compression, and exhaust processes. A valve plate is mounted on the flange exhaust port and opens and closes periodically with the compressor's intake and exhaust. When the gas pressure in the exhaust chamber reaches a certain critical value, the exhaust valve plate opens until the pressure inside the exhaust chamber is lower than the external pressure of the pump body, at which point the valve plate closes, completing one exhaust cycle of the compressor. A valve plate limiter with a certain bending lift is mounted on the back of the valve plate. This limiter restricts the opening, wrapping state, and lift of the valve plate, and significantly affects the exhaust airflow and the instantaneous speed at which the valve plate impacts the limiter, thereby affecting the compressor's performance, noise, and reliability.

[0003] With the rapid miniaturization of compressors, the operating frequency of compressors is gradually increasing. For high-frequency compressors, the operating conditions of valve plates are more severe, and the exhaust flow resistance and airflow pulsation are greatly increased. The resulting valve plate reliability, high-frequency performance, and noise issues are bottleneck problems that urgently need to be solved in the design of high-speed compressors. Summary of the Invention

[0004] The main objective of this invention is to provide a compressor exhaust assembly, a pump body assembly, a compressor, and an air conditioner, which can improve the smoothness of high-frequency exhaust of the compressor, reduce exhaust flow resistance and airflow pulsation, thereby improving the high-frequency reliability of the valve plate and playing the role of improving efficiency and reducing noise.

[0005] To achieve the above objectives, according to one aspect of the present invention, a compressor exhaust assembly is provided, disposed at a flange exhaust port, including an exhaust valve plate and a limiter. The exhaust valve plate is configured to cover the flange exhaust port, and the limiter is disposed on the side of the exhaust valve plate away from the flange exhaust port, limiting the maximum opening lift of the exhaust valve plate. The limiter includes a straight section and a curved section. The straight section is provided with a mounting hole, and the curved section is in a cantilever state. The maximum operating frequency of the compressor is f, the diameter of the flange exhaust port is d, the thickness of the limiter is T, the maximum lift of the curved section is H, the projected length of the curved section on the mounting plane of the straight section is L, the radius of curvature of the curved section is R0, the radian angle is β, and the exhaust volume of the single cavity of the compressor communicating with the flange exhaust port is V. The parameters f, β, H, L, R0, and V satisfy: 0.8 ≤ f*V / [L*(H-R0)+β*R0] 2]≤27.6, and f≥120Hz.

[0006] Furthermore, 1.4 ≤ f*V / [L*(H-R0)+β*R0 2 ≤23.5.

[0007] Furthermore, the parameters f, β, d, H, L, and R0 satisfy:

[0008] 0.15≤[L*(H-R0)+β*R0 2 ] / (π*d 2 )≤15.67.

[0009] Furthermore, 0.25 ≤ [L*(H-R0)+β*R0] 2 ] / (π*d 2 )≤12.48.

[0010] Furthermore, the parameters f, V, d, and H satisfy:

[0011] 15≤(f*V) / (d*H)≤298.

[0012] Furthermore, 28 ≤ (f*V) / (d*H) ≤ 263.

[0013] Furthermore, the parameters d and H satisfy: 2.5≤d*H≤32.4, 0.12≤H / d≤0.85.

[0014] Furthermore, 3.2≤d*H≤30.1, 0.18≤H / d≤0.64.

[0015] According to another aspect of the present invention, a pump body assembly is provided, including a flange and the above-described compressor exhaust assembly, the flange including the above-described flange exhaust port, and the compressor exhaust assembly being mounted on the flange.

[0016] According to another aspect of the present invention, a compressor is provided, comprising the above-described compressor exhaust assembly or the above-described pump body assembly.

[0017] Furthermore, the maximum operating frequency f of the compressor satisfies 120Hz≤f≤200Hz.

[0018] Furthermore, 140Hz≤f≤180Hz.

[0019] According to another aspect of the present invention, an air conditioner is provided, including a compressor, which is the compressor described above.

[0020] The compressor exhaust assembly using the technical solution of this invention includes an exhaust valve plate and a limiter. The exhaust valve plate is configured to cover the flange exhaust port. The limiter is located on the side of the exhaust valve plate away from the flange exhaust port and limits the maximum opening stroke of the exhaust valve plate. The limiter includes a straight section and a curved section. The straight section has an assembly hole, and the curved section is in a cantilever state. The maximum operating frequency of the compressor is f, the diameter of the flange exhaust port is d, the thickness of the limiter is T, the maximum stroke of the curved section is H, the projected length of the curved section on the mounting plane of the straight section is L, the radius of curvature of the curved section is R0, the radian angle is β, and the exhaust volume of the single cavity of the compressor connected to the flange exhaust port is V. The parameters f, β, H, L, R0, and V satisfy: 0.8 ≤ f*V / [L*(H-R0)+β*R0] 2 The frequency range is ≤27.6 and f≥120Hz. This compressor exhaust assembly improves the valve opening and operating conditions by optimizing the relevant structural parameters of the exhaust assembly and the valve plate structural mode, thereby improving the smoothness of high-frequency exhaust, reducing exhaust flow resistance and airflow pulsation, and thus improving the high-frequency reliability of the valve plate while also improving efficiency and reducing noise. Attached Figure Description

[0021] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0022] Figure 1 A schematic diagram of the structure of the limiter for the exhaust assembly of the compressor according to an embodiment of the present invention is shown;

[0023] Figure 2 This diagram illustrates the combined structure of the exhaust valve plate and the limiter of the exhaust assembly for a compressor according to an embodiment of the present invention.

[0024] Figure 3 A schematic diagram of the pump body assembly according to an embodiment of the present invention is shown;

[0025] Figure 4 It shows Figure 3 A magnified structural diagram at point k;

[0026] Figure 5 A schematic diagram of the cylinder structure of the pump body assembly according to an embodiment of the present invention is shown;

[0027] Figure 6 A comparison graph of the sound power level of a compressor according to an embodiment of the present invention and a compressor of related technologies is shown; and

[0028] Figure 7 A comparison curve of the energy efficiency COP of the compressor of this invention and the compressor of related technologies is shown.

[0029] The above figures include the following reference numerals:

[0030] 1. Upper flange; 11. Flange exhaust port; 2. Cylinder; 21. Intake chamber; 22. Exhaust chamber; 3. Crankshaft; 4. Roller; 5. Lower flange; 6. Sliding vane; 7. Exhaust valve plate; 8. Limiter; 81. Straight section; 82. Bending section; 9. Rivet. Detailed Implementation

[0031] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0032] See Figures 3 to 5 As shown, the pump body assembly of the rotary compressor includes main components such as upper flange 1, cylinder 2, crankshaft 3, roller 4, lower flange 5, sliding vane 6, exhaust assembly exhaust valve plate 7, and limiter 8. These components cooperate to form a sealed intake chamber 21 and exhaust chamber 22. Under the rotational drive of the crankshaft 3, the volume of the compressor intake chamber 21 and exhaust chamber 22 changes, thereby realizing the periodic intake, compression, and exhaust process of the compressor.

[0033] The flange has a flange vent 11, and an exhaust valve 7 is mounted on and covers the flange vent 11, opening and closing periodically as the compressor draws in and discharges gas. When the gas pressure in the exhaust chamber reaches a certain critical value, the exhaust valve 7 opens until the pressure in the exhaust chamber 22 is lower than the external pressure of the pump body, at which point the exhaust valve 7 closes, completing one exhaust process of the compressor.

[0034] The exhaust valve plate 7 is equipped with a valve plate limiter 8 with a certain bending stroke on its back. The exhaust valve plate 7 and the limiter 8 are stacked and fixed in sequence. The limiter 8 plays a certain limiting and constraining role on the opening, wrapping state and stroke of the exhaust valve plate 7, and greatly affects the flow of exhaust air and the instantaneous speed of the valve plate hitting the limiter, thereby affecting the compressor performance, noise and reliability.

[0035] Based on the above analysis, in order to solve the problems that occur when the compressor operates at high frequency, see [reference needed]. Figures 1 to 5As shown, according to an embodiment of the present invention, the compressor exhaust assembly is disposed at the flange exhaust port 11, including an exhaust valve plate 7 and a limiter 8. The exhaust valve plate 7 is configured to cover the flange exhaust port 11, and the limiter 8 is disposed on the side of the exhaust valve plate 7 away from the flange exhaust port 11, limiting the maximum opening lift of the exhaust valve plate 7. The limiter 8 includes a straight section 81 and a curved section 82. The straight section 81 is provided with a mounting hole, and the curved section 82 is in a cantilever state. The maximum operating frequency of the compressor is f, the diameter of the flange exhaust port 11 is d, the thickness of the limiter 8 is T, the maximum lift of the curved section 82 is H, the projected length of the curved section 82 on the mounting plane of the straight section 81 is L, the radius of curvature of the curved section 82 is R0, the radian angle is β, and the exhaust volume of the single cavity of the compressor communicating with the flange exhaust port is V. The parameters f, β, H, L, R0, and V satisfy: 0.8 ≤ f*V / [L*(H-R0)+β*R0] 2 ]≤27.6, and f≥120Hz.

[0036] This compressor exhaust assembly is designed for high-frequency compressors above 120Hz. By optimizing the relevant structural parameters of the exhaust assembly and the valve plate structure mode, it improves the valve plate opening and operating conditions, enhances the smoothness of high-frequency exhaust, reduces exhaust flow resistance and airflow pulsation, thereby improving the high-frequency reliability of the valve plate and achieving the effects of improving efficiency and reducing noise.

[0037] The exhaust volume V of the single chamber connected to the flange exhaust port 11 is the compressor displacement when the compressor is a single-cylinder compressor, and the displacement of a single cylinder connected to the flange exhaust port 11 when the compressor is a multi-cylinder compressor.

[0038] In this embodiment, the relationships between the compressor's maximum operating frequency f, the maximum lift H of the curved section 82, the projected length L of the curved section 82 on the mounting plane of the straight section 81, the radius of curvature R0 of the curved section 82, the exhaust volume V of the working chamber, and the radian angle β are defined by the above formulas, so that these parameters can influence and restrict each other, thereby achieving the beneficial effect of adapting the single-chamber exhaust volume of the working chamber of the high-frequency compressor to the overall flow space below the limiter during high-frequency operation.

[0039] In one embodiment, 1.4 ≤ f*V / [L*(H-R0)+β*R0 2 ≤23.5.

[0040] In one embodiment, the parameters f, β, d, H, L, and R0 satisfy: 0.15 ≤ [L*(H-R0) + β*R0] 2 ] / (π*d 2 )≤15.67. The exhaust volume V of the working chamber refers to the volume of the working chamber of the cylinder that is directly connected to the flange exhaust port 11.

[0041] In one embodiment, 0.25 ≤ [L*(H-R0)+β*R0] 2 ] / (π*d 2 )≤12.48.

[0042] In this embodiment, the relationships between the compressor's maximum operating frequency f, the diameter d of the flange exhaust port 11, the thickness T of the limiter 8, the maximum lift H of the curved section 82, the projected length L of the curved section 82 on the mounting plane of the straight section 81, the radius of curvature R0 of the curved section 82, and the radian angle β are defined by the above formula, so that these parameters can influence and restrict each other, thereby achieving the beneficial effect of optimizing the adaptability of the high-frequency compressor's exhaust port flow area to the overall flow space under the limiter.

[0043] In one embodiment, the exhaust volume of the working chamber of the compressor connected to the flange exhaust port 11 is V, and the parameters f, V, d, and H satisfy: 15≤(f*V) / (d*H)≤298.

[0044] In this embodiment, the relationship between the compressor's maximum operating frequency f, the diameter d of the flange exhaust port 11, the maximum lift H of the curved section 82, and the exhaust volume V of the working chamber is defined by the above formula, so that these parameters can influence and restrict each other, thereby achieving optimized design of the single-chamber exhaust volume of the high-frequency compressor during high-frequency operation and the flow area of ​​the gas after being discharged from the exhaust port and circumferentially diffused at the bottom of the baffle.

[0045] In one embodiment, 28 ≤ (f*V) / (d*H) ≤ 263.

[0046] In one embodiment, the parameters d and H satisfy: 2.5≤d*H≤32.4, 0.12≤H / d≤0.85.

[0047] In this embodiment, the relationship between the diameter d of the flange exhaust port 11 and the maximum lift H of the curved section 82 is defined by the above formula, so that these parameters can influence and restrict each other, thereby achieving optimized design of the circumferential diffusion flow area of ​​the high-frequency compressor from the exhaust port to the lower part of the limiter, and the adaptability of the circumferential diffusion flow area to the exhaust port flow area.

[0048] In one embodiment, 3.2 ≤ d*H ≤ 30.1, 0.18 ≤ H / d ≤ 0.64.

[0049] According to the above formula of the present invention, the structure of the limiter can be optimized. By optimizing the relationship values ​​of the relevant structural parameters of the exhaust component within a specific operating frequency range, the exhaust flow channel is improved, so that the exhaust flow area and exhaust flow rate have a better fit. This greatly improves the high-frequency exhaust smoothness of the pump body component, thereby reducing the exhaust flow resistance and airflow pulsation. At the same time, the instantaneous state of valve plate opening and wrapping around the limiter under high-frequency operating conditions is optimized, thereby reducing the instantaneous speed of the exhaust valve plate 7 hitting the limiter 8, improving the high-frequency reliability of the exhaust valve plate, and playing the role of improving efficiency and reducing noise.

[0050] According to an embodiment of the present invention, the pump body assembly includes a flange and the above-mentioned compressor exhaust assembly, which is disposed at the flange exhaust port 11.

[0051] The flange includes an upper flange 1 and a lower flange 5. The pump body assembly also includes a cylinder 2, a crankshaft 3, a roller 4, and a vane 6. The components cooperate to form a sealed intake chamber 21 and an exhaust chamber 22. Under the rotational drive of the crankshaft 3, the volume of the compressor intake chamber 21 and the exhaust chamber 22 changes, thereby realizing the periodic intake, compression, and exhaust process of the compressor.

[0052] The flange vent 11 is opened on the upper flange 1. The vent valve plate 7 and the limiter 8 are both provided with mounting holes. Rivets 9 are provided in the mounting holes. The rivets 9 fix the vent valve plate 7 and the limiter 8 together to the upper flange 1.

[0053] According to an embodiment of the present invention, the compressor includes the above-described compressor exhaust assembly or the above-described pump body assembly.

[0054] In one embodiment, the maximum operating frequency f of the compressor satisfies 120Hz≤f≤200Hz.

[0055] In one embodiment, 140Hz ≤ f ≤ 180Hz.

[0056] Because high-frequency compressors have a larger discharge volume and valve plate reciprocating frequency per cycle than conventional models, they are more sensitive to the exhaust flow channel. This proposal has a significant effect on high-frequency models, especially in the 140Hz to 180Hz range, where the effect is even better.

[0057] See Figure 6 and Figure 7 As shown, where Figure 6 This is a comparison curve of the sound power level of the compressor in this embodiment of the invention and a compressor in related technologies. Figure 6As can be seen from the embodiments of the present invention, when the compressor operates in the range of 120Hz≤f≤200Hz, the noise is effectively reduced compared with the related technologies, and when the compressor operates in the range of 140Hz~180Hz, the noise reduction is more obvious. Figure 7 The diagram shows a comparison of the COP (Coefficient of Performance) of the compressor according to an embodiment of the present invention with that of a compressor in related technologies. Figure 7 It can be seen that after adopting the embodiments of the present invention, when the compressor operates in the range of 120Hz≤f≤200Hz, the energy efficiency COP is improved compared with related technologies. When the compressor operates in the range of 140Hz~180Hz, the improvement in energy efficiency COP is greater and the improvement effect is more obvious.

[0058] According to an embodiment of the present invention, the air conditioner includes a compressor, which is the compressor described above.

[0059] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0060] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A compressor exhaust assembly, disposed at a flange exhaust port (11), characterized in that, The compressor includes an exhaust valve plate (7) and a limiter (8). The exhaust valve plate (7) is configured to cover the flange exhaust port (11). The limiter (8) is located on the side of the exhaust valve plate (7) away from the flange exhaust port (11) and limits the maximum opening stroke of the exhaust valve plate (7). The limiter (8) includes a straight section (81) and a curved section (82). The straight section (81) is provided with a mounting hole, and the curved section (82) is in a cantilever state. The maximum operating frequency of the compressor is f. The flange exhaust port (11) has a diameter of d, the limiter (8) has a thickness of T, the maximum lift of the curved section (82) is H, the projected length of the curved section (82) on the mounting plane of the straight section (81) is L, the radius of curvature of the curved section (82) is R0, the radian angle is β, the exhaust volume of the working chamber of the compressor connected to the flange exhaust port (11) is V, and the parameters f, β, H, L, R0, V satisfy: 0.8≤f*V / [L*(H-R0)+β*R0] 2 ]≤27.6, and f≥120Hz.

2. The exhaust assembly for a compressor according to claim 1, characterized in that, 1.4≤f*V / [L*(H-R0)+β*R0 2 ]≤23.5。 3. The exhaust assembly for a compressor according to claim 1, characterized in that, The parameters f, β, d, H, L, and R0 satisfy: 0.15≤[L*(H-R0)+β*R0 2 ] / (π*d 2 )≤15.67。 4. The exhaust assembly for a compressor according to claim 3, characterized in that, 0.25≤[L*(H-R0)+β*R0 2 ] / (π*d 2 )≤12.48。 5. The exhaust assembly for a compressor according to claim 1, characterized in that, The parameters f, V, d, and H satisfy: 15≤(f*V) / (d*H)≤298.

6. The compressor exhaust assembly according to claim 5, characterized in that, 28≤(f*V) / (d*H)≤263.

7. The exhaust assembly for a compressor according to claim 1, characterized in that, Parameters d and H satisfy: 2.5≤d*H≤32.4, 0.12≤H / d≤0.

85.

8. The exhaust assembly for a compressor according to claim 7, characterized in that, 3.2≤d*H≤30.1, 0.18≤H / d≤0.

64.

9. A pump body assembly, comprising a flange, characterized in that, It also includes a compressor exhaust assembly according to any one of claims 1 to 8, the compressor exhaust assembly being disposed at the flange exhaust port (11).

10. A compressor, characterized in that, It includes the exhaust assembly for the compressor as described in any one of claims 1 to 8 or the pump assembly as described in claim 9.

11. The compressor according to claim 10, characterized in that, The maximum operating frequency f of the compressor satisfies 120Hz≤f≤200Hz.

12. The compressor according to claim 11, characterized in that, 140Hz≤f≤180Hz.

13. An air conditioner, comprising a compressor, characterized in that, The compressor is the compressor according to any one of claims 10 to 12.

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