Exhaust check valve for a compressor and compressor having the same

Abstract

The application discloses a kind of exhaust one-way valve for compressor and the compressor with it, the exhaust one-way valve includes: valve shell assembly and valve core assembly, valve shell assembly includes valve housing and exhaust pipe, valve housing has gas outlet, the intake end of exhaust pipe is inserted in gas outlet, the cross-sectional area of intake end is S1, valve core assembly is built into valve housing, and includes movable valve core between opening position and closing position, valve core assembly has exhaust hole, exhaust passage is formed between valve core and valve housing, which is communicated between exhaust hole and gas outlet, when valve core moves to opening position, gas in valve core assembly can enter exhaust passage from exhaust hole and flow to intake end, the closest distance between valve core and valve housing is d2, the minimum flow area of exhaust passage is S2, wherein, the ratio of S1 and d2 is 8-25, and / or, the ratio of S2 and S1 is 1.2-5.The exhaust one-way valve according to the application can reduce the loss caused to the energy efficiency of the compressor.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a discharge check valve for a compressor and a compressor having the same. Background Technology

[0002] In some compressors in related technologies, a spring-loaded exhaust check valve is added to achieve differential pressure start-up. However, since the valve opening requires overcoming the spring force and the differential pressure force on the valve plate to maintain stable operation, mechanical efficiency is lost. Summary of the Invention

[0003] The present invention aims to at least solve one of the technical problems existing in the prior art. To this end, the present invention provides a discharge check valve for a compressor, which can effectively improve or avoid adverse effects on the compressor's energy efficiency.

[0004] The present invention also proposes a compressor having the above-mentioned exhaust check valve.

[0005] According to a first aspect of the present invention, a discharge check valve for a compressor includes: a valve housing assembly comprising a valve outer shell and a discharge pipe, the valve outer shell having an outlet, an inlet end of the discharge pipe being inserted into the outlet, the inlet end having a cross-sectional area of ​​S1, and the compressor being adapted to discharge air unidirectionally through the outlet end of the discharge pipe; and a valve core assembly built into the valve outer shell and including a valve core movable between an open position and a closed position, the valve core assembly having an exhaust port. An exhaust passage is formed between the valve core and the valve housing, connecting the exhaust port and the outlet. When the valve core moves to the open position, the gas in the valve core assembly can enter the exhaust passage from the exhaust port and flow to the inlet end. When the valve core moves to the open position, the closest distance between the valve core and the valve housing is d2, and the area of ​​the minimum flow surface of the exhaust passage is S2, wherein the ratio of S1 to d2 is 8 to 25, and / or the ratio of S2 to S1 is 1.2 to 5.

[0006] The exhaust check valve for a compressor according to embodiments of the present invention can reduce mechanical efficiency loss and pressure loss, and effectively improve or avoid adverse effects on the energy efficiency of the compressor.

[0007] In some embodiments, the valve core includes a cylindrical segment coaxially disposed with the air outlet. The valve core can move along the axial direction of the cylindrical segment toward the air outlet to reach the open position. The axial end of the cylindrical segment facing the air outlet is a free end. When the valve core moves to the open position, the length of the shortest line connecting the edge of the free end and the air outlet is the shortest distance d2.

[0008] In some embodiments, the cross-section of the intake end and the cross-section of the cylindrical section are both circular, and the minimum flow surface of the exhaust channel is constructed as a frustum side surface with the axis of the cylindrical section as the center line, the shortest connecting line as the generatrix, the cross-section of the outlet as the lower base, and the cross-section of the free end as the upper base.

[0009] In some embodiments, the valve housing is formed as a rotating body with the centerline of the outlet as its axis of rotation.

[0010] In some embodiments, there is at least one vent hole, and the total flow area of ​​all the vent holes is S3, wherein the ratio of S3 to S2 is 0.3 to 0.8, and / or the ratio of S3 to S1 is 1 to 2, and / or the ratio of S3 to d2 is 12 to 30.

[0011] In some embodiments, the valve core assembly includes a valve inner shell having a central hole, the valve core including a cylindrical section and a stop section, the cylindrical section passing through the central hole, the stop section being located inside the valve inner shell and connected to the inner end of the cylindrical section to restrict the inner end of the cylindrical section from dislodging from the central hole, and the exhaust holes being multiple and distributed circumferentially along the cylindrical section on the valve inner shell.

[0012] In some embodiments, the closest distance between the vent and the valve housing is d3, wherein the ratio of S1 to d3 is 8 to 25, and / or the ratio of d2 to d3 is 0.7 to 1.5.

[0013] In some embodiments, the valve core assembly defines an inner cavity, and the valve core assembly also has an air inlet. Both the air inlet and the exhaust port are connected to the inner cavity. The valve core is used to control the opening and closing of the air inlet. The flow area of ​​the air inlet is S4. There is at least one exhaust port, and the total flow area of ​​all the exhaust ports is S3. The ratio of S4 to S3 is 0.8 to 2.

[0014] In some embodiments, the valve core assembly includes a valve inner shell and a valve seat, the valve inner shell and the valve seat defining the inner cavity, the air inlet being formed on the valve seat, the air outlet being formed on the valve inner shell, and the valve core passing through the valve inner shell to reciprocate in directions away from and towards the air inlet.

[0015] In some embodiments, the valve housing mates with the valve seat to define a receiving cavity between them, and the valve inner housing is disposed within the receiving cavity.

[0016] In some embodiments, S1 is 85mm 2 -105mm 2 d2 is 5.5mm-6.5mm, and S2 is 230mm. 2 -250mm 2 .

[0017] According to a second aspect of the present invention, a compressor includes: a housing assembly, a drive assembly, a pump body assembly, and an exhaust check valve. The drive assembly and the pump body assembly are connected and both are disposed within the housing assembly. The exhaust check valve is disposed within the housing assembly and is an exhaust check valve for a compressor according to a first aspect of the present invention. The exhaust pipe passes through the housing assembly.

[0018] According to an embodiment of the present invention, by providing the exhaust check valve for the compressor described in the first aspect embodiment above, the adverse effects on the compressor's energy efficiency are reduced.

[0019] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0020] Figure 1 This is a schematic diagram of a compressor assembly according to an embodiment of the present invention;

[0021] Figure 2 yes Figure 1 The cross-sectional view shown is of the exhaust check valve in the closed state;

[0022] Figure 3 yes Figure 2 The cross-sectional view shown is of the exhaust check valve in the open position.

[0023] Figure 4 yes Figure 3 A partial enlarged view of the exhaust check valve shown;

[0024] Figure 5 yes Figure 4 A schematic diagram of the valve inner shell shown;

[0025] Figure 6 yes Figure 1 A partial schematic diagram of the compressor shown.

[0026] Figure label:

[0027] Compressor 1000;

[0028] Exhaust check valve 100;

[0029] Valve housing assembly 1; valve housing 11; air outlet 111; receiving cavity 112;

[0030] Exhaust pipe 12; Inlet end 121; Outlet end 122;

[0031] Valve core assembly 2; Valve core 21; Cylindrical section 211; Free end 2110; Stop section 212;

[0032] Valve inner shell 22; vent hole 221; center hole 222; inner cavity 223;

[0033] Valve seat 23; air inlet 231; elastic element 24; valve plate 25; screw 26;

[0034] Exhaust passage 3;

[0035] Housing assembly 200; drive assembly 300; pump body assembly 400; process pipe 500; suction pipe 600;

[0036] Liquid reservoir 2000. Detailed Implementation

[0037] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0038] The following disclosure provides numerous different embodiments or examples for implementing various structures of the invention. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the invention. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed. Additionally, examples of various specific processes and materials are provided in this invention; however, those skilled in the art will recognize the applicability of other processes and / or the use of other materials.

[0039] Hereinafter, with reference to the accompanying drawings, an exhaust check valve 100 for a compressor 1000 according to a first aspect embodiment of the present invention will be described.

[0040] like Figure 1As shown, the compressor 1000 is adapted to discharge gas unidirectionally from the inside to the outside through the discharge check valve 100. That is, when the discharge check valve 100 is open, high-pressure gas inside the compressor 1000 can be discharged to the outside of the compressor 1000 through the discharge check valve 100, while when the discharge check valve 100 is closed, fluid outside the compressor 1000 cannot flow back into the compressor 1000 through the discharge check valve 100, thereby effectively improving the operational reliability of the compressor 1000. It is worth noting that the discharge check valve 100 described herein is not a check valve integrated into the pump body assembly 400 of the compressor 1000 to control unidirectional discharge from the cylinder, but rather a check valve located outside the pump body assembly 400 and used to realize unidirectional discharge from the compressor 1000.

[0041] For example, in some embodiments, when the compressor 1000 is working, if the pressure of the high-pressure gas generated inside the compressor 1000 is sufficient, the exhaust check valve 100 can be opened to switch the exhaust check valve 100 to the open state, so that the high-pressure gas can be discharged unidirectionally to the outside of the compressor 1000 through the exhaust check valve 100 (that is, the compressor 1000 is adapted to exhaust unidirectionally through the outlet end 122 of the exhaust pipe 12 described below). When the compressor 1000 stops working, if the gas pressure inside the compressor 1000 is insufficient to open the exhaust check valve 100, the exhaust check valve 100 can be switched back to the closed state to prevent fluid outside the compressor 1000 from flowing back into the compressor 1000 through the exhaust check valve 100.

[0042] Combination Figure 2 and Figure 3 The exhaust check valve 100 includes a valve housing assembly 1, which includes a valve housing 11 and an exhaust pipe 12. The valve housing 11 has an outlet 111, and the exhaust pipe 12 has an inlet end 121 and an outlet end 122. The inlet end 121 is inserted into the outlet 111 so that the exhaust pipe 12 communicates with the interior of the valve housing 11. In this way, the gas entering the valve housing 11 can enter the inlet end 121 of the exhaust pipe 12 at the outlet 111, flow through the exhaust pipe 12, and be discharged from the outlet end 122 of the exhaust pipe 12.

[0043] It should be noted that "the air inlet 121 is inserted into the air outlet 111" means that the relative position of the air inlet 121 and the air outlet 111 is that the air inlet 121 extends into the air outlet 111, and does not limit the fixed connection method between the air inlet 121 and the air outlet 111. For example, in some embodiments, the valve housing 11 and the exhaust pipe 12 can be connected at the air inlet 121 and the air outlet 111 by welding or tube expansion connection, which will not be elaborated here.

[0044] Combination Figure 2 and Figure 3The exhaust check valve 100 also includes a valve core assembly 2, which is built into the valve housing 11. That is, at least a portion of the valve core assembly 2 is located within the valve housing 11, or the valve housing 11 covers at least a portion of the valve core assembly 2. The valve core assembly 2 includes a valve core 21, which is movable between an open position and a closed position. More specifically, the valve core 21 is movable relative to the valve housing assembly 1 in the open position (e.g., ...). Figure 3 (as shown in the image) and closed position (e.g.) Figure 2 It can move between the positions shown.

[0045] When the valve core 21 moves to the open position, the exhaust check valve 100 is in the open state, and the compressor 1000 can exhaust to the outside through the exhaust check valve 100. When the valve core 21 moves to the closed position, the exhaust check valve 100 is in the closed state, and the fluid outside the compressor 1000 cannot flow back into the compressor 1000 through the exhaust check valve 100.

[0046] like Figure 2 As shown, the valve core assembly 2 has an exhaust port 221, and an exhaust channel 3 is formed between the valve core 21 and the valve housing 11, connecting the exhaust port 221 and the air outlet 111. Figure 3 When the valve core 21 moves to the open position, the gas in the valve core assembly 2 can enter the exhaust channel 3 from the exhaust hole 221 and flow to the air inlet 121 of the exhaust pipe 12, so as to achieve the effect of exhausting the gas outward through the exhaust pipe 12 when the exhaust check valve 100 is in the open state.

[0047] like Figure 3 As shown, in some embodiments, when the valve core 21 moves to the open position, the closest distance between the valve core 21 and the valve housing 11 is d2, and the ratio of S1 to d2 is 8 to 25. S1 is the cross-sectional area of ​​the air inlet end 121 of the exhaust pipe 12 (i.e., the flow area of ​​the air inlet end 121 of the exhaust pipe 12). That is, the value range of S1 / d2 is 8 to 25. For example, S1 / d2 can be: 8, 10, 12, 14, 16, 18, 20, 22, 25, etc.

[0048] Some compressors in related technologies add a spring-loaded exhaust check valve to achieve differential pressure start-up. However, because opening the valve requires overcoming the spring force and maintaining the differential pressure on the valve plate during stable operation, mechanical efficiency is lost. According to the exhaust check valve 100 of this embodiment, when the valve core 21 moves to the open position, by limiting the ratio of S1 to d2 to 8-25, experiments show that mechanical efficiency loss and pressure loss can be effectively reduced, avoiding significant energy efficiency loss in the compressor 1000. Here, pressure loss refers to the loss of exhaust pressure relative to intake pressure in the exhaust check valve 100.

[0049] In fact, during the research and development process, the applicant creatively discovered that the flow area of ​​the exhaust check valve 100 near the exhaust position has a significant impact on mechanical efficiency loss and pressure loss. When the exhaust check valve 100 is in use, the position of the valve core 21 changes. Specifically, when the valve core 21 moves from the closed position to the open position, the minimum distance of the exhaust channel 3 formed between the valve core 21 and the valve housing 11 gradually decreases. When the valve core 21 moves to the open position, it reaches the limit value (i.e., d2) of the minimum distance between the valve core 21 and the valve housing 11. The choice of size affects the discharge volume of the exhaust check valve 100, which in turn affects the energy efficiency of the compressor 1000. Furthermore, the applicant has creatively discovered that simply limiting the value of d2 cannot effectively improve the energy efficiency of the compressor 1000. In this regard, the applicant has creatively and accidentally discovered that if d2 and the flow area S1 of the intake end 121 of the exhaust pipe 12 are designed together so that the ratio of these two values ​​meets a certain ratio range, mechanical efficiency loss and pressure loss can be unexpectedly reduced, thus avoiding a significant loss in the energy efficiency of the compressor 1000.

[0050] like Figure 3 As shown, in some embodiments, when the valve core 21 moves to the open position, the area of ​​the minimum flow surface of the exhaust passage 3 is S2, and the ratio of S2 to S1 is 1.2 to 5. S1 is the cross-sectional area of ​​the air inlet end 121 of the exhaust pipe 12 (i.e., the flow area of ​​the air inlet end 121 of the exhaust pipe 12). That is to say, the value range of S2 / S1 is 1.2 to 5. For example, S2 / S1 can be: 1.2, 1.7, 2.2, 2.7, 3.2, 3.7, 4.2, 4.7, 5, etc.

[0051] Some compressors in related technologies add a spring-loaded exhaust check valve to achieve differential pressure start-up. However, because opening the valve requires overcoming the spring force and maintaining the differential pressure on the valve plate during stable operation, mechanical efficiency is lost. According to the exhaust check valve 100 of this embodiment, when the valve core 21 moves to the open position, by limiting the ratio of S2 to S1 to 1.2 to 5, experiments show that mechanical efficiency loss and pressure loss can be effectively reduced, avoiding significant energy efficiency loss in the compressor 1000. Here, pressure loss refers to the loss of exhaust pressure relative to intake pressure in the exhaust check valve 100.

[0052] In fact, during the research and development process, the applicant creatively discovered that the flow area of ​​the exhaust check valve 100 near the exhaust position has a significant impact on mechanical efficiency loss and pressure loss. When the exhaust check valve 100 is in use, the position of the valve core 21 changes. Specifically, when the valve core 21 moves from the closed position to the open position, the minimum flow area of ​​the exhaust channel 3 formed between the valve core 21 and the valve housing 11 gradually decreases. When the valve core 21 moves to the open position, the limit value of the minimum flow area between the valve core 21 and the valve housing 11 (i.e., S2) is obtained. The choice of this size will affect the discharge volume of the exhaust check valve 100, which in turn will affect the energy efficiency of the compressor 1000. Furthermore, the applicant has creatively discovered that simply limiting the value of S2 cannot effectively improve the energy efficiency of the compressor 1000. In this regard, the applicant accidentally discovered that if S2 and the flow area S1 of the intake end 121 of the exhaust pipe 12 are designed together so that the two values ​​meet a certain ratio range, the mechanical efficiency loss and pressure loss can be unexpectedly reduced, thus avoiding a significant loss in the energy efficiency of the compressor 1000.

[0053] like Figure 3 As shown, in some embodiments, when the valve core 21 moves to the open position, the closest distance between the valve core 21 and the valve housing 11 is d2, and the area of ​​the minimum flow surface of the exhaust channel 3 is S2. The ratio of S1 to d2 is 8 to 25, and the ratio of S2 to S1 is 1.2 to 5. S1 is the cross-sectional area of ​​the air inlet end 121 of the exhaust pipe 12 (i.e., the flow area of ​​the air inlet end 121 of the exhaust pipe 12).

[0054] Some compressors in related technologies add a spring-loaded exhaust check valve to achieve differential pressure start-up. However, because opening the valve requires overcoming the spring force and maintaining the differential pressure on the valve plate during stable operation, mechanical efficiency is lost. According to the exhaust check valve 100 of this embodiment, when the valve core 21 moves to the open position, by limiting the ratio of S1 to d2 to 8-25, and the ratio of S2 to S1 to 1.2-5, experiments show that mechanical efficiency loss and pressure loss can be effectively reduced, avoiding significant energy efficiency loss in the compressor 1000. Here, pressure loss refers to the loss of exhaust pressure relative to intake pressure in the exhaust check valve 100.

[0055] In fact, during the research and development process, the applicant creatively discovered that the flow area of ​​the exhaust check valve 100 near the exhaust position has a significant impact on mechanical efficiency loss and pressure loss. When the exhaust check valve 100 is in use, the position of the valve core 21 changes. Specifically, when the valve core 21 moves from the closed position to the open position, the minimum distance and minimum flow area of ​​the exhaust channel 3 formed between the valve core 21 and the valve housing 11 gradually decrease. When the valve core 21 moves to the open position, the limit values ​​of the minimum distance (i.e., d2) and the minimum flow area (i.e., d2) between the valve core 21 and the valve housing 11 are obtained. The selection of these two dimensions (S2 and d2) affects the discharge volume of the exhaust check valve 100, which in turn affects the energy efficiency of the compressor 1000. Furthermore, the applicant creatively discovered that simply limiting the values ​​of S2 and d2 is still insufficient to effectively improve the energy efficiency of the compressor 1000. The applicant accidentally discovered that if d2 and S2 are designed in conjunction with the flow area S1 of the intake end 121 of the exhaust pipe 12, so that the values ​​of S2 / S1 and S1 / d2 simultaneously meet a certain ratio range, mechanical efficiency loss and pressure loss can be unexpectedly reduced, thus avoiding significant loss in the energy efficiency of the compressor 1000.

[0056] In summary, the exhaust check valve 100 according to the embodiments of the present invention can effectively improve or avoid the adverse effects of the exhaust check valve 100 on the energy efficiency of the compressor 1000.

[0057] In some embodiments of the present invention, such as Figure 2 and Figure 3 As shown, the valve core 21 may include a cylindrical section 211, which is coaxially arranged with the air outlet 111, meaning that the centerline of the cylindrical section 211 coincides with the centerline of the air outlet 111. The valve core 21 reciprocates along the axial direction of the cylindrical section 211. Specifically, when the valve core 21 moves along the axial direction of the cylindrical section 211 towards the direction closer to the air outlet 111 (e.g.) Figure 3 (as shown in the upward direction), the valve core 21 can move to the open position, allowing the exhaust check valve 100 to exhaust in one direction; while the valve core 21 moves along the axial direction of the cylindrical section 211 in a direction away from the outlet 111 (e.g., the upward movement), the valve core 21 can move to the open position, allowing the exhaust check valve 100 to exhaust in one direction; and when the valve core 21 moves along the axial direction of the cylindrical section 211 in a direction away from the outlet 111 (e.g., the upward movement), the valve core 21 can move to the open position, allowing the exhaust check valve 100 to exhaust in one direction; Figure 2 (As shown in the downward movement), the valve core 21 can move to the closed position, so that the exhaust check valve 100 can prevent backflow.

[0058] like Figure 3 and Figure 4As shown, the axial end of the cylindrical segment 211 facing the air outlet 111 is the free end 2110. That is, the two axial ends of the cylindrical segment 211 are one end closer to the air outlet 111 and the other end farther away from the air outlet 111, respectively. The end of the cylindrical segment 211 closer to the air outlet 111 is the free end 2110. When the valve core 21 moves to the open position (that is, when the exhaust check valve 100 is in the open state, the valve core 21 is at its maximum stroke), the length of the shortest line connecting the edge of the free end 2110 and the air outlet 111 of the valve housing 11 is the shortest distance d2 (that is, the shortest distance between the valve core 21 and the valve housing 11 when the valve core 21 moves to the open position).

[0059] Therefore, through the above design, the ratio of S1 to d2 can be designed to be the first set value more easily, and the error can be reduced more easily during assembly, further ensuring that the ratio of S1 to d2 is the first set value. At the same time, the above design can also make the exhaust more uniform, that is, the gas entering the valve housing 11 from the exhaust port 221 can flow more uniformly and quickly through the exhaust channel 3 to the intake end 121 of the exhaust pipe 12, thereby further reducing energy consumption and improving the energy efficiency of the compressor 1000.

[0060] like Figures 2-3 As shown, when "when the valve core 21 moves to the open position, the length of the shortest line between the edge of the free end 2110 and the air outlet 111 of the valve housing 11 is the shortest distance d2", in some optional examples, the cross-section of the air inlet 121 and the cross-section of the cylindrical section 211 can both be circular. The minimum flow surface of the exhaust channel 3 is constructed as follows: with the axis of the cylindrical section 211 as the center line, the shortest line as the generatrix, the cross-section of the air outlet 111 (i.e., the cross-section of the air outlet 111 at the position where the shortest line is defined) as the lower base, and the cross-section of the free end 2110 as the upper base, it is easy to calculate the area S2 of the minimum flow surface of the exhaust channel 3.

[0061] For example, refer to Figure 3 The area of ​​the cross-section at the location of the shortest connection line defined by the air outlet 111 is S5. This area is approximately equal to the cross-section of the valve housing 11 outside the pipe at the air outlet 111. For example, if the diameter of the valve housing 11 outside the pipe at the air outlet 111 is d1, then S5 = π(d1 / 2). 2 Therefore, S2 = πd2(d1 / 2 + D2 / 2), where D2 is the outer diameter of the free end 2110.

[0062] This design facilitates design, manufacturing, and assembly, ensuring that the ratio of S2 to S1 can be the second set value. Furthermore, this design allows for more uniform exhaust, meaning the gas entering the valve housing 11 from the exhaust port 221 can flow more evenly and rapidly through the exhaust channel 3 to the intake end 121 of the exhaust pipe 12, thereby further reducing energy consumption and improving the energy efficiency of the compressor 1000. It is understood that in the above example, the ratio of S2 to S1 satisfies the equation: S2 / S1=πd2(d1 / 2+D2 / 2) / =π(D1 / 2) 2 =2d2(d1+D2) / D1 2 = a, where a ranges from 1.2 to 5.

[0063] like Figures 2-3 As shown, when "the valve core 21 includes a cylindrical section 211, the cylindrical section 211 is coaxially arranged with the outlet 111, and the valve core 21 can reach the open position by moving along the axial direction of the cylindrical section 211 towards the outlet 111", in some optional examples, the valve housing 11 can be constructed as a rotating body with the center line of the outlet 111 as the axis of rotation. This facilitates design, processing, and assembly, better ensuring that the ratio of S1 to d2 is a first set value, and also better ensuring that the ratio of S2 to S1 can be a second set value. Furthermore, the above design also makes the exhaust more uniform, meaning that the gas entering the valve housing 11 from the exhaust port 221 can flow more evenly and quickly through the exhaust channel 3 to the inlet end 121 of the exhaust pipe 12, thereby further reducing energy consumption and improving the energy efficiency of the compressor 1000.

[0064] In some embodiments of the present invention, such as Figure 3 and Figure 5 As shown, there can be at least one exhaust port 221, and the total flow area of ​​all exhaust ports 221 is S3, wherein the ratio of S3 to S2 is 0.3 to 0.8 (condition 1), and / or the ratio of S3 to S1 is 1 to 2 (condition 2), and / or the ratio of S3 to d2 is 12 to 30 (condition 3). That is, satisfying at least one of the above three conditions—that is, satisfying only one condition, satisfying any two conditions simultaneously, or satisfying all three conditions simultaneously—can effectively improve or avoid the adverse effects of the exhaust check valve 100 on the energy efficiency of the compressor 1000. Satisfying any two conditions can further improve or avoid the adverse effects of the exhaust check valve 100 on the energy efficiency of the compressor 1000. And satisfying all three conditions simultaneously can more effectively improve or avoid the adverse effects of the exhaust check valve 100 on the energy efficiency of the compressor 1000.

[0065] The ratio of S3 to S2 being 0.3 to 0.8 (condition 1) means that the value of S3 / S2 ranges from 0.3 to 0.8. For example, S3 / S2 can be 0.3, 0.4, 0.5, 0.6, 0.7, 0.8, etc. The ratio of S3 to S1 being 1 to 2 (condition 2) means that the value of S3 / S1 ranges from 1 to 2. For example, S3 / S1 can be 1, 1.2, 1.4, 1.6, 1.8, 2, etc. The ratio of S3 to d2 being 12 to 30 (condition 3) means that the value of S3 / d2 ranges from 12 to 30. For example, S3 / d2 can be 12, 15, 18, 21, 24, 27, 30, etc.

[0066] In fact, during the research and development process, the applicant creatively discovered that the flow area S3 of the exhaust one-way valve 100 at the exhaust port 221 also has some impact on mechanical efficiency loss and pressure loss, which in turn affects the energy efficiency of the compressor 1000. Furthermore, the applicant creatively discovered that simply limiting the value of S3 cannot effectively improve the energy efficiency of the compressor 1000. In this regard, the applicant creatively and accidentally discovered that if at least one of S2 / S1 and S1 / d2 is limited, and at least one of S3 / S2, S3 / S1, and S3 / d2 is also limited to meet the above-mentioned corresponding value range, mechanical efficiency loss and pressure loss can be unexpectedly further reduced, thus avoiding a significant loss in the energy efficiency of the compressor 1000.

[0067] In some embodiments of the present invention, such as Figure 4 and Figure 5 As shown, the valve core assembly 2 includes a valve inner shell 22 with a central hole 222. The valve core 21 includes a cylindrical section 211 and a stop section 212. The cylindrical section 211 passes through the central hole 222, and the stop section 212 is located inside the valve inner shell 22 and connected to the inner end of the cylindrical section 211 to prevent the inner end of the cylindrical section 211 from exiting the central hole 222. Multiple exhaust holes 221 are distributed circumferentially along the cylindrical section 211 on the valve inner shell 22. This improves exhaust uniformity and efficiency, avoids related technical problems caused by concentrated exhaust, and prevents insufficient local structural strength of the valve inner shell 22 due to the single exhaust hole 221 having a large opening area. Therefore, while ensuring the total flow area S3 of all exhaust holes 221 meets the above requirements, the structural reliability and compactness of the valve inner shell 22 are improved, the service life of the exhaust check valve 100 is increased, and the miniaturization requirements of the exhaust check valve 100 are met.

[0068] It is worth noting that the number of exhaust holes 221 is not limited, for example, it can be 2 to 8, such as 2, 4, 6, 8, etc. When there are 6 exhaust holes 221 and they are evenly distributed in the valve inner shell 22, and when the valve inner shell 22 is a rotating body, the requirement of central symmetry of exhaust holes 221 is also met, which can better balance the total exhaust area and the structural reliability of the valve inner shell 22.

[0069] In some embodiments of the present invention, such as Figure 3 As shown, the closest distance between the exhaust port 221 and the valve housing 11 is d3, where the ratio of S1 to d3 is 8–25, and / or the ratio of d2 to d3 is 0.7–1.5. That is, only one of the ratios "S1 to d3 = 8–25" and "d2 to d3 = 0.7–1.5" can be satisfied, or both can be satisfied simultaneously. Therefore, satisfying either one can effectively improve or avoid the adverse effects of the exhaust check valve 100 on the energy efficiency of the compressor 1000. Satisfying either two can further improve or avoid the adverse effects of the exhaust check valve 100 on the energy efficiency of the compressor 1000.

[0070] The ratio of S1 to d3 being 8–25 means that the value of S1 / d3 ranges from 8 to 25. For example, S1 / d3 can be 8, 10, 12, 14, 16, 18, 20, 22, 25, etc. Similarly, the ratio of d2 to d3 being 0.7–1.5 means that the value of d2 / d3 ranges from 0.7 to 1.5. For example, d2 / d3 can be 0.7, 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, 1.4, 1.5, etc.

[0071] In fact, during the research and development process, the applicant creatively discovered that the closest distance d3 between the exhaust port 221 and the valve housing 11 also has some impact on mechanical efficiency loss and pressure loss, which in turn affects the energy efficiency of the compressor 1000. Furthermore, the applicant creatively discovered that simply limiting the value of d3 still cannot effectively improve the energy efficiency of the compressor 1000. In this regard, the applicant creatively and accidentally discovered that if at least one of S2 / S1 and S1 / d2 is limited, and at least one of S1 / d3 and d2 / d3 is also limited to meet the above-mentioned corresponding value range, mechanical efficiency loss and pressure loss can be unexpectedly further reduced, thus avoiding a significant loss in the energy efficiency of the compressor 1000.

[0072] In some embodiments of the present invention, such as Figures 2-4As shown, the valve core assembly 2 defines an inner cavity 223. The valve core assembly 2 also has an air inlet 231, which, along with an exhaust port 221, communicates with the inner cavity 223. The valve core 21 controls the opening and closing of the air inlet 231. Specifically, when the valve core 21 moves to the open position, it releases the air inlet 231, allowing high-pressure gas to enter the inner cavity 223 through the air inlet 231 and then flow out into the valve housing 11 through the normally open exhaust port 221. At this time, the exhaust check valve 100 is in the open state. Conversely, when the valve core 21 moves to the closed position, it directly or indirectly blocks the air inlet 231, thus closing it and preventing backflow of gas. The exhaust check valve 100 is in the closed state. Therefore, the exhaust check valve 100 has a simple structure and is easy to control. Of course, the present invention is not limited thereto. In other embodiments of the present invention, the valve core 21 may also be configured as a switch for controlling the exhaust port 221, etc.

[0073] In some examples, such as Figure 3 and Figure 4 As shown, the flow area of ​​the intake port 231 is S4, and there is at least one exhaust port 221, with a total flow area of ​​S3 for all exhaust ports 221. The ratio of S4 to S3 is 0.8 to 2. That is, the value of S4 / S3 ranges from 0.8 to 2. For example, S4 / S3 can be: 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, 1.4, 1.5, 1.6, 1.7, 1.8, 1.9, 2, etc. Therefore, the adverse effects of the exhaust check valve 100 on the energy efficiency of the compressor 1000 can be effectively improved or avoided.

[0074] In fact, during the research and development process, the applicant creatively discovered that the flow area of ​​the air inlet 231, S4, also has some impact on mechanical efficiency loss and pressure loss, which in turn affects the energy efficiency of the compressor 1000. Furthermore, the applicant creatively discovered that simply limiting the value of S4 cannot effectively improve the energy efficiency of the compressor 1000. In this regard, the applicant creatively and accidentally discovered that if at least one of S2 / S1 and S1 / d2 is limited, and S4 / S3 is limited to 0.8 to 2, mechanical efficiency loss and pressure loss can be unexpectedly further reduced, thus avoiding a significant loss in the energy efficiency of the compressor 1000.

[0075] In some embodiments of the present invention, such as Figures 2-4As shown, the valve core assembly 2 may include a valve inner shell 22 and a valve seat 23. An inner cavity 223 is defined between the valve inner shell 22 and the valve seat 23. An air inlet 231 is formed on the valve seat 23, and an exhaust port 221 is formed on the valve inner shell 22. The valve core 21 passes through the valve inner shell 22 and reciprocates in directions away from and towards the air inlet 231. Specifically, when the valve core 21 moves towards the air inlet 231, it reaches the closed position, and when the valve core 21 moves away from the air inlet, it reaches the open position. Therefore, the valve core assembly 2 has a simple and compact structure, high operational reliability, is easy to process and assemble, and has low production costs.

[0076] Optionally, such as Figure 3 and Figure 4 As shown, the valve core 21 may include a cylindrical section 211 and a stop section 212. A central hole 222 is formed on the valve inner shell 22. The cylindrical section 211 passes through the central hole 222. The stop section 212 is located inside the valve inner shell 22 and is connected to the inner end of the cylindrical section 211 to prevent the inner end of the cylindrical section 211 from dislodging from the central hole 222. The centerline of the valve core 21 is the centerline of the stop section 212, which coincides with the centerline of the air inlet 231. The valve core assembly 2 also includes an elastic element 24, which is disposed between the valve inner shell 22 and the stop section 212 to apply an elastic restoring force toward the stop section 212 toward the air inlet 231, thereby driving the valve core 21 to move toward the closed position.

[0077] For example, in some alternative embodiments, such as Figure 3 and Figure 4 As shown, the elastic element 24 can be a cylindrical spring and sleeved outside the cylindrical section 211, thereby facilitating the acquisition and installation of the elastic element 24 and effectively reducing the problem of the elastic element 24 detaching from the valve core 21. This improves the operational reliability of the elastic element 24. Of course, the present invention is not limited to this. For example, in other embodiments of the present invention, springs of other shapes or elastic air bladders can be used instead of cylindrical springs.

[0078] For example, in some alternative embodiments, such as Figure 3 and Figure 4As shown, the valve core assembly 2 may further include a valve plate 25, which is located on the side of the stop section 212 away from the cylindrical section 211. Projected along the centerline of the cylindrical section 211, the projected area of ​​the valve plate 25 is larger than the projected area of ​​the stop section 212, and also larger than the projected area of ​​the air inlet 231. Therefore, the valve core 21 can close the air inlet 231 through the valve plate 25. This minimizes the size of the stop section 212 of the valve core 21, requiring only that the stop section 212 restrict the valve core 21 from disengaging from the central hole 222. The air inlet 231 can be opened directly without blocking or closing it. This way, even if the flow area of ​​the air inlet 231 is large, there is no need to increase the cross-sectional area of ​​the stop section 212. This avoids the problem that the cross-sectional area of ​​the stop section 212 needs to be larger due to the influence of the air inlet 231. Furthermore, it avoids the problem that the large cross-sectional area of ​​the stop section 212 occupies more space in the valve inner shell 22, affecting the air capacity of the inner cavity 223 and the exhaust of the exhaust port 221. This effectively improves the overall performance of the exhaust check valve 100.

[0079] Furthermore, it is understandable that when the overall axial height of the valve core 21 is determined, the axial height of the stop section 212 can be controlled to control the range of motion of the cylindrical section 211, so that the closest distance d2 between the valve core 21 and the valve housing 11 and the area S2 of the minimum flow surface of the exhaust channel 3 can meet the design requirements. On the other hand, the thickness of the valve plate 25 can be controlled to be thinner, reducing the space occupied by the valve plate 25 in the valve inner shell 22 and the impact on the exhaust of the exhaust port 221, thereby improving the overall performance of the exhaust check valve 100.

[0080] Furthermore, the connection method between the valve plate 25 and the valve core 21 is not limited, for example, in Figure 3 and Figure 4 In the specific example shown, a through hole can be provided on the valve plate 25, and a threaded hole can be provided on the valve core 21. A screw 26 passing through from the valve plate 25 to the valve core 21 can be used to connect the two, thus achieving a simple and effective reliable connection between the valve plate 25 and the valve core 21. Of course, the present invention is not limited to this. For example, in other embodiments of the present invention, the connection can also be achieved through welding, expansion joints, etc., which will not be elaborated here.

[0081] Furthermore, such as Figures 2-4As shown, the valve housing 11 mates with the valve seat 23, defining a receiving cavity 112 between the valve housing 11 and the valve seat 23. The valve inner shell 22 is disposed within the receiving cavity 112. This simplifies the structure, saves components, improves the overall structural compactness of the exhaust check valve 100, and reduces costs. Of course, the invention is not limited to this. For example, in other embodiments of the invention, a base plate may mate with the valve housing 11 to define the receiving cavity 112, with both the valve seat 23 and the valve inner shell 22 disposed within the receiving cavity 112, etc., which will not be elaborated here.

[0082] For example, in some alternative embodiments of the invention, such as Figure 3 As shown, when the exhaust pipe 12 is a circular pipe and the outlet 111 of the valve housing 11 is a circular opening, the outer diameter of the valve housing 11 at the outlet 111 can be d1, and the inner diameter of the inlet end 121 of the exhaust pipe 12 is D1. By limiting the range of the difference between d1 and D1, it can be ensured that the inlet end 121 of the exhaust pipe 12 and the outlet 111 of the valve housing 11 can be reliably connected. For example, in some optional examples, d1-D1 is 4mm-10mm, such as 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, or 10mm.

[0083] In summary, based on the energy efficiency loss of the compressor 1000 caused by the exhaust check valve 100, this application sets at least one of S2 / S1 and S1 / d2 to meet the corresponding value range, and sets at least one of S3 / S2, S3 / S1, S3 / d2, S1 / d3, d2 / d3, and S4 / S3 to meet the corresponding value range, thereby unexpectedly reducing mechanical efficiency loss and pressure loss, and avoiding the significant energy efficiency loss of the compressor 100 caused by the exhaust check valve 100.

[0084] For example, in some optional examples, the value of S1 ranges from 85mm. 2 -105mm 2 For example, it could be 85mm 2 90mm 2 95mm 2 100mm 2 105mm 2 Wait, the value range of d2 is 5.5mm-6.5mm, for example, it can be 5.5mm, 5.7mm, 5.9mm, 6.1mm, 6.3mm, 6.5mm, etc., and the value range of S2 is 230mm. 2 -250mm 2 For example, it could be 230mm 2 235mm 2 240mm 2 245mm 2 250mm2 And so on. Therefore, the above S2 / S1 and S1 / d2 can be satisfied to meet the corresponding value range, thereby unexpectedly reducing mechanical efficiency loss and pressure loss, and avoiding the large loss of energy efficiency of compressor 100 caused by exhaust check valve 100.

[0085] For example, in some alternative examples, the air inlet 231 on the valve seat 23 is a circular hole with a diameter of D4, and the free end 2110 of the valve core 21 has a circular cross-section with a diameter of D2, d1 = 16.4 mm, D1 = 11 mm, and S2 = 240 mm. 2 S1 = 95mm 2 d2 = 6.1 mm, S3 = 120 mm 2 d3 = 5.8 mm, S4 = 145 mm 2 D2 = 9mm, D4 = 13.6mm. Therefore, all the above ratios (S2 / S1, S1 / d2, S3 / S2, S3 / S1, S3 / d2, S1 / d3, d2 / d3, S4 / S3) are within their respective ranges, which unexpectedly reduces mechanical efficiency loss and pressure loss, avoiding significant energy efficiency losses to the compressor 1000 caused by the exhaust check valve 100. Of course, the specific values ​​of the above parameters are only examples and may fluctuate to some extent, as long as the ratios of the corresponding parameters meet the corresponding ranges. This will not be elaborated further here.

[0086] The compressor 1000 according to a second aspect embodiment of the present invention will now be described.

[0087] Specifically, the compressor 1000 according to an embodiment of the present invention may include: a housing assembly 200, a drive assembly 300, and a pump assembly 400. The drive assembly 300 and the pump assembly 400 are both disposed within the housing assembly 200. The drive assembly 300 is connected to the pump assembly 400 to drive the pump assembly 400 to perform compression work.

[0088] It should be noted that the specific type of compressor 1000 is not limited. For example, in some embodiments, when compressor 1000 is a rotary compressor 1000, pump body assembly 400 may include a cylinder with a cylinder chamber and a piston inside the cylinder chamber. The specific configuration of drive assembly 300 is not limited. For example, it may include a motor and a drive shaft. The motor may be an internal rotor motor or an external rotor motor. The rotor is connected to the drive shaft so that when the motor is working, the rotor drives the drive shaft to rotate. The drive shaft has an eccentric portion, and the piston is sleeved on the eccentric portion so that the piston can roll along the cavity wall of the cylinder chamber when the drive shaft rotates. Furthermore, it should be noted that the specific configuration of pump body assembly 400 is not limited to this. For example, in some embodiments, the cylinder assembly may further include bearings disposed on both sides of the cylinder, etc., which will not be elaborated here.

[0089] The compressor 1000 according to an embodiment of the present invention may further include a discharge check valve 100 according to a first aspect embodiment of the present invention. The discharge check valve 100 is disposed within the housing assembly 200, and the discharge pipe 12 passes through the housing assembly 200. Thus, by providing the discharge check valve 100, the loss of energy efficiency of the compressor 1000 can be reduced.

[0090] In some embodiments, such as Figure 1 and Figure 4 As shown, the exhaust check valve 100 can be housed within the housing assembly 200 of the compressor 1000 and directly or indirectly mounted on the housing assembly 200. The exhaust pipe 12 can penetrate the housing assembly 200 of the compressor 1000, thereby allowing the high-pressure gas inside the compressor 1000 to be discharged unidirectionally to the outside of the housing assembly 200 through the exhaust pipe 12. This simplifies the structure, making the compressor 1000 more compact, effectively protecting the exhaust check valve 100 from damage, facilitating installation, and reducing costs. It is worth noting that in the embodiments of this invention, the exhaust pipe 12 can be a single, continuous pipe or a combination pipe composed of several pipe segments; no limitation is imposed here.

[0091] Based on the above description, in some embodiments of the present invention, when the compressor 1000 is operating, the high-pressure gas inside the housing assembly 200 of the compressor 1000 pushes open the valve plate 25, and the exhaust check valve 100 is in the open state. The high-pressure gas enters the inner cavity 223 of the valve inner shell 22 through the inlet port 231, and then enters the receiving cavity 112 of the valve outer shell 11 through the exhaust port 221. Afterwards, it is discharged to the outside of the housing assembly 200 through the exhaust pipe 12, thus realizing a normal refrigeration cycle. When the compressor 1000 stops operating, the valve plate 25 closes the inlet port 231 under the action of the elastic element 24, and the exhaust check valve 100 is in the closed state. The gas in the inner cavity 223 cannot flow back into the housing assembly 200 (i.e., the space inside the housing assembly 200 other than the exhaust check valve 100) through the inlet port 231, which is beneficial for the compressor 1000 to quickly achieve pressure balance and meet the requirements for rapid restart. At the same time, it can prevent refrigerant from depositing inside the compressor 1000, thus avoiding the decrease in lubricating oil viscosity caused by excessive refrigerant dissolving in the oil sump at the bottom of the compressor 1000. This, in turn, prevents abnormal wear that might result from decreased lubricating oil viscosity inside the compressor 1000 when the compressor 1000 restarts, improving the reliability of the compressor 1000. Furthermore, it can reduce heat loss and improve operating efficiency.

[0092] Additionally, it should be noted that the specific configuration of the housing assembly 200 according to embodiments of the present invention is not limited. For example, when the compressor 1000 is a vertical compressor 1000, the housing may include a main housing and an upper housing and a lower housing disposed at the upper and lower ends of the main housing. In this case, in some embodiments, the exhaust one-way valve 100 may be disposed on the upper housing, and the exhaust pipe 12 may pass through the upper housing. However, the present invention is not limited to this. When the compressor 1000 is a horizontal compressor 1000, the housing may include a main housing and a left housing and a right housing disposed at the left and right ends of the main housing. In this case, in some embodiments, the exhaust one-way valve 100 may be disposed at the top of the main housing, and the exhaust pipe 12 may pass through the main housing, etc., and so on. Examples will not be given here. According to some embodiments of the present invention, such as Figure 1 As shown, a process tube 500 can also be provided on the housing assembly 200. During production, the process tube 500 can be used for production processes such as oil sealing and vacuuming. This facilitates the processing of the housing assembly 200.

[0093] Other components of the compressor 1000 according to embodiments of the present invention, such as the suction pipe 600, and its operation, are known to those skilled in the art and will not be described in detail here. Furthermore, in some embodiments of the compressor 1000 according to embodiments of the present invention, such as... Figure 1 As shown, the compressor 1000 assembly can be formed by connecting the suction pipe 600 to the liquid receiver 2000. The compressor 1000 assembly can be applied to refrigeration equipment, such as refrigerators and air conditioners. Since the performance of the compressor 1000 is improved, the overall performance of these refrigeration devices can be improved, which will not be elaborated here. Other configurations and operations of the refrigeration equipment according to embodiments of the present invention are known to those skilled in the art and will not be described in detail here.

[0094] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0095] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0096] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0097] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0098] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0099] Although embodiments of the invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A discharge check valve for a compressor, characterized in that, The exhaust check valve includes: A valve housing assembly, comprising a valve housing and an exhaust pipe, wherein the valve housing has an outlet, the inlet end of the exhaust pipe is inserted into the outlet, the cross-sectional area of ​​the inlet end is S1, and the compressor is adapted to unidirectionally exhaust gas through the outlet end of the exhaust pipe. A valve core assembly, built into the valve housing, includes a valve core movable between an open position and a closed position. The valve core assembly has an exhaust port, and an exhaust passage is formed between the valve core and the valve housing, communicating between the exhaust port and the air outlet. When the valve core moves to the open position, gas within the valve core assembly can enter the exhaust passage from the exhaust port and flow towards the air inlet. When the valve core moves to the open position, the closest distance between the valve core and the valve housing is d2, and the area of ​​the minimum flow surface of the exhaust channel is S2, wherein the ratio of S1 to d2 is 8 to 25, and / or the ratio of S2 to S1 is 1.2 to 5; the valve core includes a cylindrical section, which is coaxially arranged with the air outlet, and the valve core can reach the open position by moving along the axial direction of the cylindrical section toward the air outlet, and the axial end of the cylindrical section facing the air outlet is a free end, and when the valve core moves to the open position, the length of the shortest line between the edge of the free end and the air outlet is the closest distance d2; the cross-section of the air inlet end and the cross-section of the cylindrical section are both circular, and the minimum flow surface of the exhaust channel is constructed as: a frustum-shaped side surface with the axis of the cylindrical section as the center line, the shortest line as the generatrix, the cross-section of the air outlet as the lower base, and the cross-section of the free end as the upper base.

2. The exhaust check valve for a compressor according to claim 1, characterized in that, The valve housing is formed as a rotating body with the center line of the air outlet as the axis of rotation.

3. The exhaust check valve for a compressor according to claim 1, characterized in that, There is at least one exhaust port, and the total flow area of ​​all the exhaust ports is S3, wherein the ratio of S3 to S2 is 0.3 to 0.8, and / or the ratio of S3 to S1 is 1 to 2, and / or the ratio of S3 to d2 is 12 to 30.

4. The exhaust check valve for a compressor according to claim 3, characterized in that, The valve core assembly includes a valve inner shell with a central hole. The valve core includes a cylindrical section and a stop section. The cylindrical section passes through the central hole, and the stop section is located inside the valve inner shell and connected to the inner end of the cylindrical section to restrict the inner end of the cylindrical section from exiting the central hole. The exhaust holes are multiple and distributed circumferentially along the cylindrical section on the valve inner shell.

5. The exhaust check valve for a compressor according to claim 1, characterized in that, The closest distance between the exhaust port and the valve housing is d3, wherein the ratio of S1 to d3 is 8 to 25, and / or the ratio of d2 to d3 is 0.7 to 1.

5.

6. The exhaust check valve for a compressor according to claim 1, characterized in that, The valve core assembly defines an inner cavity, and the valve core assembly also has an air inlet. Both the air inlet and the exhaust port are connected to the inner cavity. The valve core is used to control the opening and closing of the air inlet. The flow area of ​​the air inlet is S4. There is at least one exhaust port, and the total flow area of ​​all the exhaust ports is S3. The ratio of S4 to S3 is 0.8 to 2.

7. The exhaust check valve for a compressor according to claim 6, characterized in that, The valve core assembly includes a valve inner shell and a valve seat, with the inner shell and the valve seat defining the inner cavity. The air inlet is formed on the valve seat, and the air outlet is formed on the valve inner shell. The valve core passes through the valve inner shell and reciprocates in a direction away from and towards the air inlet.

8. The exhaust check valve for a compressor according to claim 7, characterized in that, The valve housing mates with the valve seat to define a receiving cavity between them, and the valve inner housing is disposed within the receiving cavity.

9. The exhaust check valve for a compressor according to any one of claims 1-8, characterized in that, S1 is 85mm 2 -105mm 2 d2 is 5.5mm-6.5mm, and S2 is 230mm. 2 -250mm 2 .

10. A compressor, characterized in that, include: The compressor includes a housing assembly, a drive assembly, a pump body assembly, and an exhaust check valve. The drive assembly and the pump body assembly are connected and both are disposed within the housing assembly. The exhaust check valve is disposed within the housing assembly and is an exhaust check valve for a compressor according to any one of claims 1-9. The exhaust pipe passes through the housing assembly.

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