CN116263160A

CN116263160A - Exhaust check valve for compressor and compressor with same

Info

Publication number: CN116263160A
Application number: CN202111531460.3A
Authority: CN
Inventors: 魏琪青; 高斌; 钟志锋
Original assignee: Guangdong Meizhi Compressor Co Ltd; Guangdong Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd; Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date: 2021-12-14
Filing date: 2021-12-14
Publication date: 2023-06-16
Also published as: WO2023108924A1

Abstract

The invention discloses a discharge check valve for a compressor and a compressor with the same, wherein the discharge check valve comprises: the valve casing is provided with an air outlet, an air inlet end of the air outlet is inserted into the air outlet, the cross section area of the air inlet end is S1, the valve core assembly is arranged in the valve casing and comprises a valve core which can move between an opening position and a closing position, an air exhaust hole is formed in the valve core assembly, an air exhaust channel which is communicated between the air exhaust hole and the air outlet is formed between the valve core assembly and the valve casing, when the valve core moves to the opening position, air in the valve core assembly can enter the air exhaust channel from the air exhaust hole and flow to the air inlet end, the nearest distance between the valve core and the valve casing is d2, the area of the minimum overflow surface of the air exhaust channel is S2, the ratio of S1 to d2 is 8-25, and/or the ratio of S2 to S1 is 1.2-5. The exhaust check valve can reduce the loss of energy efficiency of the compressor.

Description

Exhaust check valve for compressor and compressor with same

Technical Field

The invention relates to the technical field of compressors, in particular to an exhaust one-way valve for a compressor and the compressor with the same.

Background

Some compressors in the related art add a discharge check valve with a spring in order to implement a pressure difference starting function, but mechanical efficiency is lost due to the fact that the valve needs to be opened to overcome a spring force and a pressure difference force of a valve plate when the valve is kept in a stable operation.

Disclosure of Invention

The present invention aims to solve at least one of the technical problems existing in the prior art. The invention is based on the object of providing a discharge check valve for a compressor, which can more effectively improve or avoid the adverse effects on the energy efficiency of the compressor.

The invention also provides a compressor with the exhaust one-way valve.

According to an embodiment of the first aspect of the present invention, a discharge check valve for a compressor includes: the valve housing assembly comprises a valve housing and an exhaust pipe, the valve housing is provided with an air outlet, the air inlet end of the exhaust pipe is inserted and matched with the air outlet, the cross section area of the air inlet end is S1, and the compressor is suitable for unidirectional exhaust through the air outlet end of the exhaust pipe; the valve core assembly is arranged in the valve shell and comprises a valve core which can move between an opening position and a closing position, an exhaust hole is formed in the valve core assembly, an exhaust channel which is communicated between the exhaust hole and the air outlet is formed between the valve core and the valve shell, when the valve core moves to the opening position, air in the valve core assembly can enter the exhaust channel from the exhaust hole and flow to the air inlet end, when the valve core moves to the opening position, the nearest distance between the valve core and the valve shell is d2, the area of the minimum flow surface of the exhaust channel is S2, the ratio of S1 to d2 is 8-25, and/or the ratio of S2 to S1 is 1.2-5.

According to the exhaust check valve for the compressor, disclosed by the embodiment of the invention, the mechanical efficiency loss and the pressure loss can be reduced, and the adverse effect on the energy efficiency of the compressor can be effectively improved or avoided.

In some embodiments, the valve core includes a cylindrical section, the cylindrical section is coaxially disposed with the air outlet, the valve core moves along an axial direction of the cylindrical section towards a direction approaching the air outlet to reach the open position, an axial end of the cylindrical section towards the air outlet is a free end, and when the valve core moves to the open position, a length of a shortest connecting line between an edge of the free end and the air outlet is the nearest distance d2.

In some embodiments, 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 air outlet channel is configured to: the axis of the cylindrical section is taken as a central line, the shortest connecting line is taken as a bus, the cross section of the air outlet is taken as a lower bottom, and the cross section of the free end is taken as the side surface of the truncated cone with an upper bottom.

In some embodiments, the valve housing is formed as a revolution body with a center line of the air outlet as a revolution axis.

In some embodiments, the number of the exhaust holes is at least one, and the total overflow area of all the exhaust holes is S3, wherein the ratio of S3 to S2 is 0.3-0.8, and/or the ratio of S3 to S1 is 1-2, and/or the ratio of S3 to d2 is 12-30.

In some embodiments, the valve core assembly comprises an inner valve shell, the inner valve shell is provided with a central hole, the valve core comprises a cylindrical section and a stop section, the cylindrical section is arranged in the inner valve shell in a penetrating mode, the stop section is connected with the inner end of the cylindrical section to limit the inner end of the cylindrical section from falling out of the central hole, and the exhaust holes are distributed on the inner valve shell in a plurality of circumferential directions of the cylindrical section.

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.

In some embodiments, the valve core assembly defines an inner cavity, the valve core assembly further has an air inlet hole, the air inlet hole and the air outlet hole are both communicated with the inner cavity, the valve core is used for controlling the opening and closing of the air inlet hole, the flow area of the air inlet hole is S4, the number of the air outlet holes is at least one, and the total flow area of all the air outlet holes is S3, wherein the ratio of S4 to S3 is 0.8-2.

In some embodiments, the valve core assembly includes a valve inner housing and a valve seat defining the inner chamber therebetween, the air intake hole is formed on the valve seat, the air exhaust hole is formed on the valve inner housing, and the valve core is penetrated through the valve inner housing to reciprocate in a direction away from and toward the air intake hole.

In some embodiments, the valve outer housing cooperates with the valve seat to define a receiving chamber with the valve seat, and the valve inner housing is disposed within the receiving chamber.

In some embodiments, S1 is 85mm ² -105mm ² D2 is 5.5mm to 6.5mm and S2 is 230mm ² -250mm ² 。

According to a second aspect of the present invention, a compressor includes: the compressor comprises a shell component, a driving component, a pump body component and an exhaust one-way valve, wherein the driving component is connected with the pump body component and is arranged in the shell component, the exhaust one-way valve is arranged in the shell component and is an exhaust one-way valve for a compressor according to the embodiment of the first aspect of the invention, and the exhaust pipe penetrates through the shell component.

According to the compressor of the embodiment of the invention, the exhaust check valve for the compressor of the embodiment of the first aspect is arranged, so that adverse effects on energy efficiency of the compressor are reduced.

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.

Drawings

FIG. 1 is a schematic view of a compressor assembly according to one embodiment of the invention;

FIG. 2 is a cross-sectional view of the exhaust check valve shown in FIG. 1 in a closed state;

FIG. 3 is a cross-sectional view of the exhaust check valve shown in FIG. 2 in an open state;

FIG. 4 is an enlarged partial view of the exhaust check valve shown in FIG. 3;

FIG. 5 is a schematic view of the valve inner housing shown in FIG. 4;

fig. 6 is a partial schematic view of the compressor shown in fig. 1.

Reference numerals:

a compressor 1000;

an exhaust check valve 100;

a valve housing assembly 1; a valve housing 11; an air outlet 111; a housing chamber 112;

an exhaust pipe 12; an intake end 121; an outlet end 122;

a valve core assembly 2; a valve element 21; cylindrical section 211; a free end 2110; a stop section 212;

a valve inner housing 22; an exhaust hole 221; a central bore 222; an inner cavity 223;

a valve seat 23; an air intake hole 231; an elastic member 24; a valve plate 25; a screw 26;

an exhaust passage 3;

a housing assembly 200; a drive assembly 300; a pump body assembly 400; a process tube 500; an air suction pipe 600;

a reservoir 2000.

Detailed Description

Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative and intended to explain the present invention and should not be construed as limiting the invention.

The following disclosure provides many different embodiments, or examples, for implementing different structures of the invention. In order to simplify the present disclosure, components and arrangements of specific examples are described below. They are, of course, merely examples and are not intended to limit the invention. Furthermore, the present invention may repeat reference numerals and/or letters in the various examples. This repetition is for the purpose of simplicity and clarity and does not in itself dictate a relationship between the various embodiments and/or configurations discussed. In addition, the present invention provides examples of various specific processes and materials, but one of ordinary skill in the art will recognize the applicability of other processes and/or the use of other materials.

Next, a discharge check valve 100 for a compressor 1000 according to a first aspect of the present invention will be described with reference to the accompanying drawings.

As shown in fig. 1, the compressor 1000 is adapted to discharge air unidirectionally from inside to outside through the discharge check valve 100. That is, when the discharge check valve 100 is in an open state, high pressure gas in the compressor 1000 may be discharged to the outside of the compressor 1000 through the discharge check valve 100, and when the discharge check valve 100 is in a closed state, fluid outside the compressor 1000 may not flow back into the compressor 1000 through the discharge check valve 100, so that the operational reliability of the compressor 1000 may be effectively improved. It should be noted that the exhaust check valve 100 described herein is not a check valve integrated in the pump body assembly 400 of the compressor 1000 for controlling the unidirectional exhaust of the cylinder, but a check valve located outside the pump body assembly 400 for realizing the outward exhaust of the compressor 1000.

For example, in some embodiments, when the compressor 1000 is in operation, the pressure of the high-pressure gas generated in the compressor 1000 is sufficient, the discharge check valve 100 may be pushed open, so that the discharge check valve 100 is switched to an open state, and thus the high-pressure gas may be discharged out of the compressor 1000 through the discharge check valve 100 in one direction (i.e., the compressor 1000 is suitable for unidirectional discharge through the discharge end 122 of the discharge pipe 12 described later), and when the compressor 1000 is stopped, the gas pressure in the compressor 1000 is insufficient to push open the discharge check valve 100, the discharge check valve 100 may be switched back to a closed state, so as to prevent the fluid out of the compressor 1000 from flowing back into the compressor 1000 through the discharge check valve 100.

Referring to fig. 2 and 3, the exhaust check valve 100 includes a valve housing assembly 1, the valve housing assembly 1 includes a valve housing 11 and an exhaust pipe 12, the valve housing 11 has an air outlet 111, the exhaust pipe 12 has an air inlet end 121 and an air outlet end 122, and the air inlet end 121 is inserted into the air outlet 111 so that the exhaust pipe 12 communicates with the interior of the valve housing 11, so that air entering the valve housing 11 can enter the air inlet end 121 of the exhaust pipe 12 at the air outlet 111 and be discharged from the air outlet end 122 of the exhaust pipe 12 after flowing through the exhaust pipe 12.

It should be noted that, the "the air inlet end 121 is inserted into the air outlet 111" means that the relative position between the air inlet end 121 and the air outlet 111 is that the air inlet end 121 extends into the air outlet 111, and is not limited to a fixed connection manner between the air inlet end 121 and the air outlet 111, for example, in some embodiments, a valve housing 11 and an exhaust pipe 12 may be connected between the air inlet end 121 and the air outlet 111 by welding, or by expansion connection, etc., which will not be repeated herein.

Referring to fig. 2 and 3, the exhaust check valve 100 further includes a valve core assembly 2, where the valve core assembly 2 is disposed in the valve housing 11, that is, at least a portion of the valve core assembly 2 is disposed in the valve housing 11, or the valve housing 11 is covered outside at least a portion of the valve core assembly 2. The valve spool assembly 2 includes a valve spool 21, the valve spool 21 being movable between an open position and a closed position, and more specifically, the valve spool 21 being movable relative to the valve housing assembly 1 between an open position (e.g., the position shown in fig. 3) and a closed position (e.g., the position shown in fig. 2).

When the valve element 21 moves to the open position, the discharge check valve 100 is in an open state, the compressor 1000 can discharge air outwards through the discharge check valve 100, and when the valve element 21 moves to the closed position, the discharge check valve 100 is in a closed state, and fluid outside the compressor 1000 cannot flow backwards into the compressor 1000 through the discharge check valve 100.

As shown in fig. 2, the valve core assembly 2 has an exhaust hole 221, an exhaust channel 3 communicating between the exhaust hole 221 and the air outlet 111 is formed between the valve core 21 and the valve housing 11, and when the valve core 21 moves to the open position, with reference to fig. 3, the air in the valve core assembly 2 may enter the exhaust channel 3 from the exhaust hole 221 and flow to the air inlet end 121 of the exhaust pipe 12, so as to achieve the effect of exhausting air through the exhaust pipe 12 when the exhaust check valve 100 is in the open state.

As shown in fig. 3, in some embodiments, when the spool 21 moves to the open position, the closest distance between the spool 21 and the valve housing 11 is d2, the ratio of S1 to d2 is 8 to 25, and S1 is the cross-sectional area of the intake end 121 of the exhaust pipe 12 (i.e., the area of the flow through of the intake end 121 of the exhaust pipe 12). That is, the value of S1/d2 ranges from 8 to 25, for example, S1/d2 may be: 8. 10, 12, 14, 16, 18, 20, 22, 25, etc.

Some compressors in the related art add a discharge check valve with a spring in order to implement a pressure difference starting function, but mechanical efficiency is lost due to the fact that the valve needs to be opened to overcome a spring force and a pressure difference force of a valve plate when the valve is kept in a stable operation. According to the exhaust check valve 100 of the embodiment of the present invention, when the valve core 21 moves to the open position, experiments show that the ratio of S1 to d2 is limited to 8-25, so that the mechanical efficiency loss and the pressure loss can be effectively reduced, and the energy efficiency of the compressor 1000 is prevented from generating a larger loss. The pressure loss refers to a loss of the exhaust pressure of the exhaust check valve 100 relative to the intake pressure.

In fact, the applicant has creatively found that the flow area of the exhaust check valve 100 in the vicinity of the exhaust position has a great influence on the mechanical efficiency loss and the pressure loss during development, and that the position of the valve body 21 changes during use of the exhaust check valve 100, and in particular, that the minimum distance of the exhaust passage 3 formed between the valve body 21 and the valve housing 11 gradually decreases as the valve body 21 moves from the closed position to the open position, and that when the valve body 21 moves to the open position, a limit value (i.e., d 2) of the minimum distance between the valve body 21 and the valve housing 11 is obtained, and that this size selection influences the exhaust amount of the exhaust check valve 100, and thus the energy efficiency of the compressor 1000, and further that the value of d2 alone is limited, the energy efficiency of the compressor 1000 is not yet effectively improved, and that, in this way, if the ratio of d2 to the excess flow area S1 of the intake end 121 of the exhaust pipe 12 is designed in combination, the applicant has creatively and accidentally found that the ratio satisfies a certain ratio range, and thus the mechanical efficiency and the pressure loss can be reduced and the energy efficiency loss of the compressor 1000 can be prevented from being greatly lost.

As shown in fig. 3, in some embodiments, when the valve element 21 moves to the open position, the area of the minimum flow surface of the exhaust passage 3 is S2, the ratio of S2 to S1 is 1.2-5, and S1 is the cross-sectional area of the intake end 121 of the exhaust pipe 12 (i.e., the flow area of the intake end 121 of the exhaust pipe 12). That is, the value of S2/S1 ranges from 1.2 to 5, for example, S2/S1 may be: 1.2, 1.7, 2.2, 2.7, 3.2, 3.7, 4.2, 4.7, 5, etc.

Some compressors in the related art add a discharge check valve with a spring in order to implement a pressure difference starting function, but mechanical efficiency is lost due to the fact that the valve needs to be opened to overcome a spring force and a pressure difference force of a valve plate when the valve is kept in a stable operation. According to the exhaust check valve 100 of the embodiment of the present invention, when the valve core 21 moves to the open position, experiments show that the ratio of S2 to S1 is limited to 1.2-5, so that the mechanical efficiency loss and the pressure loss can be effectively reduced, and the energy efficiency of the compressor 1000 is prevented from being greatly lost. The pressure loss refers to a loss of the exhaust pressure of the exhaust check valve 100 relative to the intake pressure.

In fact, the applicant has creatively found that the flow area of the exhaust check valve 100 in the vicinity of the exhaust position has a great influence on the mechanical efficiency loss and the pressure loss during development, the position of the valve spool 21 changes when the exhaust check valve 100 is in use, and in particular, the minimum flow area of the exhaust passage 3 formed between the valve spool 21 and the valve housing 11 gradually decreases when the valve spool 21 moves from the closed position to the open position, and when the valve spool 21 moves to the open position, a limit value (S2) of the minimum flow area between the valve spool 21 and the valve housing 11 is obtained, and this size selection influences the exhaust amount of the exhaust check valve 100, thereby influencing the energy efficiency of the compressor 1000, and further, the applicant has creatively found that only the value of S2 is limited, but the energy efficiency of the compressor 1000 cannot be effectively improved, and in this regard, the applicant has accidentally found that if the value of S2 and the flow area S1 of the intake end 121 of the exhaust pipe 12 are combined so that the two values satisfy a certain ratio range, thereby the mechanical efficiency and the pressure loss can be reduced, and the energy efficiency loss of the compressor 1000 can be prevented from being unexpectedly large.

As shown in fig. 3, in some embodiments, when the valve element 21 moves to the open position, the closest distance between the valve element 21 and the valve housing 11 is d2, the area of the smallest flow-through surface of the exhaust passage 3 is S2, where the ratio of S1 to d2 is 8-25, and at the same time, the ratio of S2 to S1 is 1.2-5, and S1 is the cross-sectional area of the intake end 121 of the exhaust pipe 12 (i.e., the flow-through area of the intake end 121 of the exhaust pipe 12).

Some compressors in the related art add a discharge check valve with a spring in order to implement a pressure difference starting function, but mechanical efficiency is lost due to the fact that the valve needs to be opened to overcome a spring force and a pressure difference force of a valve plate when the valve is kept in a stable operation. According to the exhaust check valve 100 of the embodiment of the invention, when the valve core 21 moves to the open position, the ratio of S1 to d2 is limited to 8-25, and meanwhile, the ratio of S2 to S1 is limited to 1.2-5, so that experiments prove that the mechanical efficiency loss and the pressure loss can be effectively reduced, and the energy efficiency of the compressor 1000 is prevented from generating larger loss. The pressure loss refers to a loss of the exhaust pressure of the exhaust check valve 100 relative to the intake pressure.

In fact, the applicant has creatively found that the flow area of the exhaust check valve 100 in the vicinity of the exhaust position has a great influence on the mechanical efficiency loss and the pressure loss, and that the position of the valve body 21 changes when the exhaust check valve 100 is in use, and specifically that the minimum distance and the minimum flow area of the exhaust passage 3 formed between the valve body 21 and the valve housing 11 decrease gradually when the valve body 21 moves from the closed position to the open position, and that the limit value of the minimum distance (i.e., d 2) and the limit value of the minimum flow area (i.e., S2) between the valve body 21 and the valve housing 11 are obtained when the valve body 21 moves to the open position, and that the selection of these two dimensions affects the exhaust amount of the exhaust check valve 100, and thus affects the energy efficiency of the compressor 1000, and further that the applicant has creatively found that the energy efficiency of the compressor 1000 is not improved effectively only by limiting the values of S2 and d2, and that the accidental design of the ratio S1 and S2 with the flow area S1 of the intake end 121 of the exhaust pipe 12 is simultaneously achieved, and that the mechanical efficiency loss is avoided by accident, and the loss is greatly reduced.

In summary, according to the exhaust check valve 100 of the embodiment of the present invention, the adverse effect of the exhaust check valve 100 on the energy efficiency of the compressor 1000 can be effectively improved or avoided.

In some embodiments of the present invention, as shown in fig. 2 and 3, the valve spool 21 may include a cylindrical section 211, the cylindrical section 211 being disposed coaxially with the air outlet port 111, that is, a center line of the cylindrical section 211 coincides with a center line of the air outlet port 111. When the spool 21 reciprocates in the axial direction of the cylindrical section 211, specifically, when the spool 21 moves in the axial direction of the cylindrical section 211 toward the direction approaching the air outlet port 111 (for example, upward movement as shown in fig. 3), the spool 21 can move to the open position so that the exhaust check valve 100 can exhaust unidirectionally; and when the valve spool 21 moves in the axial direction of the cylindrical section 211 in a direction away from the air outlet port 111 (e.g., downward movement as shown in fig. 2), the valve spool 21 can move to the closed position, so that the exhaust check valve 100 can prevent backflow.

As shown in fig. 3 and 4, the axial end of the cylindrical section 211 facing the air outlet 111 is a free end 2110, that is, the axial ends of the cylindrical section 211 are respectively an end close to the air outlet 111 and an end far from the air outlet 111, wherein the end of the cylindrical section 211 close to the air outlet 111 is the free end 2110, and the shortest connecting line between 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) when the valve core 21 moves to the open position (that is, the valve core 21 is at the maximum stroke).

Therefore, through the design, the ratio of S1 to d2 can be designed to be the first set value more easily, and the error is reduced more easily during assembly, so that the ratio of S1 to d2 is further ensured to be the first set value, and meanwhile, through the design, the exhaust can be more uniform, namely, the gas entering the valve housing 11 from the exhaust hole 221 can flow to the air inlet end 121 of the exhaust pipe 12 more uniformly and rapidly through the exhaust channel 3, thereby further reducing the energy consumption and improving the energy efficiency of the compressor 1000.

As shown in fig. 2-3, when 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 closest distance d2 when the spool 21 moves to the open position, in some alternative examples, both the cross-section of the air inlet end 121 and the cross-section of the cylindrical section 211 may be circular, with the minimum flow-through surface of the air outlet channel 3 configured to: the area S2 of the minimum flow-through surface of the exhaust passage 3 can be easily calculated by taking the axis of the cylindrical section 211 as the center line, taking the shortest connecting line as the bus bar, taking the cross section of the air outlet 111 (i.e., the cross section of the air outlet 111 at the position where the shortest connecting line is defined) as the bottom, and taking the cross section of the free end 2110 as the side of the truncated cone of the upper bottom.

For example, referring to fig. 3, the area of the cross section of the outlet port 111 at the position defining the shortest connecting line is S5, which is approximately equal to the outside cross section of the orifice of the valve housing 11 at the outlet port 111, for example, the outside diameter of the orifice of the valve housing 11 at the outlet port 111 is d1, then s5=pi (d 1/2) ² . Thus, s2=pi D2 (D1/2+d2/2), where D2 is the outer diameter of the free end 2110.

Therefore, the design, the processing and the assembly are more convenient, the ratio of S2 to S1 can be ensured to be the second set value, and meanwhile, the exhaust can be more uniform through the design, namely, the gas entering the valve shell 11 from the exhaust hole 221 can flow to the air inlet end 121 of the exhaust pipe 12 more uniformly and rapidly through the exhaust channel 3, so that the energy consumption is further reduced, and the energy efficiency of the compressor 1000 is improved. It will be appreciated that in the above example, the ratio of S2 to S1 may satisfy the equation: s2/s1=pi D2 (D1/2+d2/2)/=pi (D1/2) ² ＝2d2(d1+D2)/D1 ² The value range of the value of the component A is 1.2-5.

As shown in fig. 2 to 3, when the spool 21 includes a cylindrical section 211, the cylindrical section 211 being disposed coaxially with the air outlet port 111, and the spool 21 is movable in the axial direction of the cylindrical section 211 toward the direction approaching the air outlet port 111 to the open position, the valve housing 11 may be configured as a revolution body with the center line of the air outlet port 111 as a revolution axis in some alternative examples. Therefore, the design, the processing and the assembly are convenient, the ratio of S1 to d2 is better ensured to be a first set value, the ratio of S2 to S1 is better ensured to be a second set value, and the exhaust can be more uniform through the design, namely, the gas entering the valve shell 11 from the exhaust hole 221 can flow to the air inlet end 121 of the exhaust pipe 12 more uniformly and rapidly through the exhaust channel 3, thereby further reducing the energy consumption and improving the energy efficiency of the compressor 1000.

In some embodiments of the present invention, as shown in fig. 3 and 5, the exhaust hole 221 may be at least one, and the total flow area of all the exhaust holes 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, at least one of the above three conditions may be satisfied, only one condition may be satisfied, any two conditions may be satisfied, and three conditions may be satisfied at the same time. Thus, when either of the conditions is satisfied, the adverse effect of the discharge check valve 100 on the energy efficiency of the compressor 1000 can be more effectively improved or avoided. When either two of these conditions are satisfied, the adverse effect of the discharge check valve 100 on the energy efficiency of the compressor 1000 can be further improved or avoided. When the above three conditions are simultaneously satisfied, the adverse effect of the discharge check valve 100 on the energy efficiency of the compressor 1000 can be more effectively improved or avoided.

Wherein the ratio of S3 to S2 is 0.3 to 0.8 (condition 1) means that: the value range of S3/S2 is 0.3-0.8, for example, S3/S2 can be: 0.3, 0.4, 0.5, 0.6, 0.7, 0.8, etc. Wherein, the ratio of S3 to S1 is 1-2 (condition 2) refers to: the value range of S3/S1 is 1-2, for example, S3/S1 can be: 1. 1.2, 1.4, 1.6, 1.8, 2, etc. Wherein the ratio of S3 to d2 is 12 to 30 (condition 3) means that: the value range of S3/d2 is 12-30, for example, S3/d2 can be: 12. 15, 18, 21, 24, 27, 30, etc.

Indeed, the applicant has creatively found that the flow area S3 of the discharge check valve 100 at the discharge hole 221 has some influence on the mechanical efficiency loss and the pressure loss, which in turn affect the energy efficiency of the compressor 1000, and further has creatively found that the limiting of the value of S3 alone does not effectively improve the energy efficiency of the compressor 1000, and has creatively and accidentally found that if at least one of S2/S1 and S1/d2 is well limited and at least one of S3/S2, S3/S1 and S3/d2 is redefined, the mechanical efficiency loss and the pressure loss can be unexpectedly further reduced, and the energy efficiency of the compressor 1000 is prevented from generating larger loss.

In some embodiments of the present invention, as shown in fig. 4 and 5, the valve core assembly 2 includes a valve inner case 22, the valve inner case 22 having a central hole 222 thereon, the valve core 21 including a cylindrical section 211 and a stopper section 212, the cylindrical section 211 being provided through the central hole 222, the stopper section 212 being located inside the valve inner case 22 and connected to an inner end of the cylindrical section 211 to restrict the inner end of the cylindrical section 211 from being separated from the central hole 222, the exhaust hole 221 being plural and distributed on the valve inner case 22 in a circumferential direction of the cylindrical section 211. Therefore, the exhaust uniformity can be improved, the exhaust efficiency is improved, the related technical problems caused by centralized exhaust are avoided, and the problem that the local structural strength of the valve inner shell 22 is insufficient due to the fact that the exhaust holes 221 are only one and the opening area is large can also be avoided, so that the structural reliability and the structural compactness of the valve inner shell 22 can be improved on the premise that the total overflow area S3 of all the exhaust holes 221 meets the requirements, the service life of the exhaust check valve 100 is prolonged, and the miniaturized development requirements of the exhaust check valve 100 are met.

It should be noted that the number of the exhaust holes 221 is not limited, and may be, for example, 2 to 8, for example, 2, 4, 6, 8, etc. When the number of the exhaust holes 221 is 6 and the exhaust holes are uniformly formed in the valve inner shell 22, and when the valve inner shell 22 is a revolution body, the requirement of the central symmetry of the exhaust holes 221 is met, and the total exhaust area and the structural reliability of the valve inner shell 22 can be better considered.

In some embodiments of the present invention, as shown in fig. 3, the closest distance between the exhaust hole 221 and the valve housing 11 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. That is, only one of "the ratio of S1 to d3 is 8 to 25" and "the ratio of d2 to d3 is 0.7 to 1.5" may be satisfied, or both of "the ratio of S1 to d3 is 8 to 25" and "the ratio of d2 to d3 is 0.7 to 1.5" may be satisfied. Thus, when either one of them is satisfied, the adverse effect of the discharge check valve 100 on the energy efficiency of the compressor 1000 can be more effectively improved or avoided. And when any two of them are satisfied, the adverse effect of the discharge check valve 100 on the energy efficiency of the compressor 1000 can be further improved or avoided.

Wherein, the ratio of S1 to d3 is 8-25, which means that: the value range of S1/d3 is 8-25, for example, S1/d3 can be: 8. 10, 12, 14, 16, 18, 20, 22, 25, etc. Wherein, the ratio of d2 to d3 is 0.7-1.5, which means that: the value of d2/d3 ranges from 0.7 to 1.5, for example, d2/d3 may be: 0.7, 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, 1.4, 1.5, etc.

Indeed, the applicant has creatively found during the development that the closest distance d3 between the exhaust hole 221 and the valve housing 11 has some influence on the mechanical efficiency loss and the pressure loss, which in turn affects the energy efficiency of the compressor 1000, and further has creatively found that limiting the value of d3 alone does not effectively improve the energy efficiency of the compressor 1000, and has creatively and accidentally found that if at least one of S2/S1 and S1/d2 is well limited and at least one of S1/d3 and d2/d3 is redefined at the same time, the mechanical efficiency loss and the pressure loss can be unexpectedly further reduced, and the energy efficiency of the compressor 1000 is prevented from being greatly lost.

In some embodiments of the present invention, as shown in fig. 2-4, the valve core assembly 2 defines an inner cavity 223, the valve core assembly 2 further has an air inlet 231 thereon, the air inlet 231 and the air outlet 221 are both communicated with the inner cavity 223, and the valve core 21 is used for controlling the opening and closing of the air inlet 231. When the valve element 21 moves to the open position, the valve element 21 releases the air inlet 231 to open the air inlet 231, high-pressure air can enter the inner cavity 223 through the air inlet 231 and then flows out into the valve housing 11 through the normally open air outlet 221, the air exhaust check valve 100 is in the open state, and when the valve element 21 moves to the closed position, the valve element 21 directly or indirectly seals the air inlet 231, so that the air inlet 231 is closed, air cannot flow back through the air inlet 231, and the air exhaust check valve 100 is in the closed state. Thus, the exhaust check valve 100 has a simple structure and is easy to control. Of course, the present invention is not limited thereto, and in other embodiments of the present invention, the valve body 21 may be provided as a switch or the like for controlling the exhaust hole 221.

In some examples, as shown in fig. 3 and 4, the air intake hole 231 has an overflow area S4, the air discharge hole 221 has at least one, and the total overflow area of all the air discharge holes 221 is S3, wherein the ratio of S4 to S3 is 0.8-2. That is, the value of S4/S3 ranges from 0.8 to 2, for example, S4/S3 may 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. Thus, the adverse effect of the discharge check valve 100 on the energy efficiency of the compressor 1000 can be effectively improved or avoided.

In fact, the applicant has creatively found that the flow area of the air intake hole 231S 4 has some influence on the mechanical efficiency loss and the pressure loss, and thus the energy efficiency of the compressor 1000, and further has creatively found that the energy efficiency of the compressor 1000 cannot be effectively improved by limiting the value of S4 only, and has creatively and accidentally found that if at least one of S2/S1 and S1/d2 is limited, and S4/S3 is limited to 0.8-2, the mechanical efficiency loss and the pressure loss can be unexpectedly further reduced, and the energy efficiency of the compressor 1000 is prevented from being greatly lost.

In some embodiments of the present invention, as shown in fig. 2 to 4, the valve core assembly 2 may include a valve inner case 22 and a valve seat 23, an inner chamber 223 is defined between the valve inner case 22 and the valve seat 23, an intake hole 231 is formed on the valve seat 23, an exhaust hole 221 is formed on the valve inner case 22, and the valve core 21 is penetrated through the valve inner case 22 to reciprocate in a direction away from and toward the intake hole 231, specifically, a closed position may be reached when the valve core 21 moves in a direction toward the intake hole 231, and an open position may be reached when the valve core 21 moves in a direction away from the intake hole. Therefore, the valve core assembly 2 has the advantages of simple and compact structure, high action reliability, easy processing and assembly and low production cost.

Alternatively, as shown in fig. 3 and 4, 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 case 22, the cylindrical section 211 is penetrated through the central hole 222, the stop section 212 is located in the valve inner case 22 and connected with the inner end of the cylindrical section 211 to limit the inner end of the cylindrical section 211 from being separated from the central hole 222, wherein the center line of the valve core 21 is the center line of the stop section 212, and the center line coincides with the center line of the air inlet hole 231. The valve cartridge assembly 2 further includes an elastic member 24, the elastic member 24 being provided between the valve inner case 22 and the stopper section 212 to apply an elastic restoring force to the stopper section 212 toward the air intake hole 231 to thereby drive the valve cartridge 21 to move toward the closed position.

For example, in some alternative embodiments, as shown in fig. 3 and 4, the elastic element 24 may be a cylindrical spring and sleeved outside the cylindrical section 211, so as to facilitate the acquisition of the elastic element 24 and the installation of the elastic element 24, and effectively reduce the problem that the elastic element 24 is separated from the valve core 21. The operational reliability of the elastic element 24 is improved. Of course, the present invention is not limited thereto, and for example, in other embodiments of the present invention, other shapes of springs, elastic bladders, or the like may be employed instead of the cylindrical springs.

For example, in some alternative embodiments, as shown in fig. 3 and 4, the valve core assembly 2 may further include a valve plate 25, where the valve plate 25 is disposed on a side of the stop section 212 away from the cylindrical section 211, and is projected forward along the center line 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 the projected area of the valve plate 25 is larger than the projected area of the air inlet 231, so that the valve core 21 may close the air inlet 231 through the valve plate 25, thereby reducing the size of the stop section 212 of the valve core 21 as much as possible, and the stop section 212 only needs to meet the requirement of limiting the valve core 21 to separate from the central hole 222, and does not need to be able to block and close the air inlet 231, so that even if the flow area of the air inlet 231 is larger, there is no need to increase the cross-sectional area of the stop section 212, so that the problem that the cross-sectional area of the stop section 212 is larger, the space inside the inner shell 22 is occupied, the air capacity of the inner cavity 223 is affected, and the air outlet 221 is affected, so that the overall performance of the exhaust check valve 100 is effectively improved.

Furthermore, it will be appreciated that when the overall axial height of the valve core 21 is determined, the axial height of the stop section 212 may be controlled, so that, on one hand, the movement range of the cylindrical section 211 is controlled, and 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 passage 3 may meet the design requirements, on the other hand, the thickness of the valve sheet 25 may be controlled to be thinner, so that the occupation of the space in the valve inner housing 22 by the valve sheet 25 is reduced, and the exhaust of the exhaust hole 221 is affected, thereby improving the overall performance of the exhaust check valve 100.

In addition, the connection between the valve plate 25 and the valve body 21 is not limited, and for example, in the specific example shown in fig. 3 and 4, a hole may be provided in the valve plate 25, and a threaded hole may be provided in the valve body 21, and both may be connected by using a screw 26 penetrating in the direction from the valve plate 25 to the valve body 21, so that reliable connection between the valve plate 25 and the valve body 21 is simply and effectively achieved. Of course, the present invention is not limited thereto, and for example, in other embodiments of the present invention, the connection between the two may be implemented by welding, tube expansion connection, etc., which will not be described herein.

Further, as shown in fig. 2 to 4, the valve outer housing 11 is engaged with the valve seat 23, the valve outer housing 11 and the valve seat 23 define a receiving chamber 112 therebetween, and the valve inner housing 22 is provided in the receiving chamber 112. Thus, the structure can be simplified, parts can be saved, the overall structural compactness of the exhaust check valve 100 can be improved, and the cost can be reduced. Of course, the present invention is not limited thereto, for example, in other embodiments of the present invention, the bottom plate and the valve housing 11 may be used to define the accommodating cavity 112, the valve seat 23 and the valve inner housing 22 are both disposed in the accommodating cavity 112, and so on, which is not described herein.

For example, in some alternative embodiments of the present invention, as shown in fig. 3, when the exhaust pipe 12 is a circular pipe and the air outlet 111 of the valve housing 11 is a circular port, the outer diameter of the orifice of the valve housing 11 at the air outlet 111 may be D1, and the inner diameter of the air inlet end 121 of the exhaust pipe 12 may be D1, and by limiting the range of the difference between D1 and D1, it may be ensured that the air inlet end 121 of the exhaust pipe 12 and the air outlet 111 of the valve housing 11 may be reliably connected. For example, in some alternative examples, D1-D1 is 4mm-10mm, e.g., D1-D1 may be 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, 10mm.

In summary, based on the energy efficiency loss of the compressor 1000 caused by the exhaust check valve 100, the present application sets at least one of S2/S1 and S1/d2 to conform to the corresponding value range, and sets at least one of S3/S2, S3/S1, S3/d2, S1/d3, d2/d3 and S4/S3 to conform to the corresponding value range, so that the mechanical efficiency loss and the pressure loss can be unexpectedly reduced, and the larger loss of the energy efficiency of the compressor 1000 caused by the exhaust check valve 100 is avoided.

For example, in some alternative examples, S1 has a value in the range of 85mm ² -105mm ² For example, 85mm ² ，90mm ² ，95mm ² ，100mm ² ，105mm ² Etc., d2 has a value in the range of 5.5mm to 6.5mm, for example, 5.5mm,5.7mm,5.9mm,6.1mm,6.3mm,6.5mm, etc., and S2 has a value in the range of 230mm ² -250mm ² For example, 230mm ² ，235mm ² ，240mm ² ，245mm ² ，250mm ² And so on. Therefore, the S2/S1 and S1/d2 can be better satisfied to meet the corresponding value range, so that the mechanical efficiency loss and the pressure loss can be accidentally reduced, and the great loss of the energy efficiency of the compressor 1000 caused by the exhaust check valve 100 is avoided.

For example, in some alternative examples, the inlet aperture 231 on the valve seat 23 is a circular aperture and has a diameter D4, the free end 2110 of the valve core 21 is circular in cross-section and has a diameter D2, d1=16.4 mm, d1=11 mm, s2=240 mm ² ，S1＝95mm ² ，d2＝6.1mm，S3＝120mm ² ，d3＝5.8mm，S4＝145mm ² D2=9mm, d4=13.6 mm. Therefore, the above-mentioned all ratios (S2/S1, S1/d2, S3/S1, S3/d2, S1/d3, d2/d3, S4/S3) can be better satisfied, and the corresponding value ranges are met, so that the mechanical efficiency loss and the pressure loss can be unexpectedly reduced, and the larger loss of the energy efficiency of the compressor 1000 caused by the exhaust check valve 100 can be avoided. Of course, the specific values of the above parameters are only examples, and may have certain fluctuation, as long as the ratio of the corresponding parameters is satisfied to meet the corresponding valuesThe range is only needed, and the description is omitted here.

Next, a compressor 1000 according to an embodiment of the second aspect of the present invention is described.

Specifically, the compressor 1000 according to an embodiment of the present invention may include: the device comprises a shell assembly 200, a driving assembly 300 and a pump body assembly 400, wherein the driving assembly 300 and the pump body assembly 400 are arranged in the shell assembly 200, and the driving assembly 300 is connected with the pump body assembly 400 to drive the pump body assembly 400 to execute compression work.

It should be noted that the specific type of the compressor 1000 is not limited, for example, in some embodiments, when the compressor 1000 is a rotary compressor 1000, the pump body assembly 400 may include a cylinder having a cylinder chamber therein with a piston disposed therein. The driving assembly 300 may include, for example, a motor and a driving shaft, the motor may be an inner rotor type motor or an outer rotor type motor, the rotor is connected to the driving shaft to drive the driving shaft to rotate through the rotor when the motor is in operation, the driving shaft has an eccentric portion, and the piston is sleeved on the eccentric portion so that the piston can roll along a cavity wall of the cylinder cavity when the driving shaft rotates. In addition, it should be noted that the specific configuration of the pump body assembly 400 is not limited thereto, for example, in some embodiments, the cylinder assembly may further include bearings disposed on two sides of the cylinder, and the like, which is not described herein.

The compressor 1000 according to the embodiment of the present invention may further include the discharge check valve 100 according to the embodiment of the first aspect of the present invention, the discharge check valve 100 is disposed in the casing assembly 200, and the discharge pipe 12 is disposed through the casing assembly 200. Thus, by providing the discharge check valve 100, the loss of energy efficiency of the compressor 1000 can be improved.

In some embodiments, as shown in fig. 1 and 4, the discharge check valve 100 may be received in the shell assembly 200 of the compressor 1000 and mounted directly or indirectly on the shell assembly 200 of the compressor 1000, and the discharge pipe 12 may penetrate the shell assembly 200 of the compressor 1000 so that high pressure gas in the compressor 1000 may be discharged unidirectionally to the outside of the shell assembly 200 of the compressor 1000 through the discharge pipe 12. Therefore, the structure can be simplified, the compressor 1000 is compact, the exhaust check valve 100 is effectively protected from damage, the installation is convenient, and the cost is reduced. It should be noted that, in the embodiment of the present invention, the exhaust pipe 12 may be a complete pipe, or may be a combined pipe formed by splicing several pipe sections, which is not limited herein.

Based on the above description, in some embodiments of the present invention, when the compressor 1000 is operated, the high pressure gas in the casing assembly 200 of the compressor 1000 pushes up the valve sheet 25, the discharge check valve 100 is in an open state, the high pressure gas enters the inner cavity 223 of the valve inner case 22 through the gas inlet hole 231, then enters the receiving cavity 112 of the valve outer case 11 through the gas outlet hole 221, and then is discharged outside the casing assembly 200 through the gas outlet pipe 12, thereby realizing a normal refrigeration cycle. When the compressor 1000 stops working, the valve plate 25 closes the air inlet 231 under the action of the elastic element 24, the exhaust one-way valve 100 is in a closed state, and the air in the inner cavity 223 cannot flow back into the casing assembly 200 (namely, the space except the exhaust one-way valve 100 in the casing assembly 200) through the air inlet 231, so that the compressor 1000 can realize pressure balance rapidly, and the requirement of quick restarting is met. Meanwhile, the refrigerant in the compressor 1000 can be prevented from depositing, so that the viscosity of the lubricating oil is prevented from being reduced due to the fact that too much refrigerant is dissolved in an oil pool at the bottom of the compressor 1000, and further, when the compressor 1000 is started again, abnormal abrasion possibly caused by the viscosity reduction of the lubricating oil in the compressor 1000 is prevented, and the reliability of the compressor 1000 is improved. In addition, heat loss can be reduced, and the operation efficiency is improved.

In addition, it should be noted that the specific configuration of the casing assembly 200 according to the embodiment of the present invention is not limited, and for example, when the compressor 1000 is a vertical compressor 1000, the casing may include a main casing and upper and lower casings provided at upper and lower ends of the main casing, and in this case, in some embodiments, the exhaust check valve 100 may be provided on the upper casing while the exhaust pipe 12 is penetrated through the upper casing. However, the present invention is not limited thereto, and when the compressor 1000 is a horizontal type compressor 1000, the casing may include a main casing and left and right casings provided at left and right ends of the main casing, in which case, in some embodiments, the discharge check valve 100 may be provided at the top of the main casing while the discharge pipe 12 is penetrated through the main casing, etc., which is not exemplified herein. According to some embodiments of the present invention, as shown in fig. 1, the process tube 500 may be further disposed on the cabinet assembly 200, and the process tube 500 may be used for oil sealing, vacuum pumping, etc. during production. Thereby facilitating processing of the cabinet assembly 200.

Other constructions of the compressor 1000, such as the suction pipe 600, etc., and operation thereof according to embodiments of the present invention are known to those of ordinary skill in the art, and will not be described in detail herein. In addition, in some embodiments, as shown in fig. 1, the compressor 1000 may be connected to the liquid storage 2000 through the air suction pipe 600 to form a compressor 1000 assembly, and the compressor 1000 assembly may be applied to refrigeration devices, such as refrigerators, air conditioners, etc., and the performance of the compressor 1000 may be improved, so that the overall performance of the refrigeration devices may be improved, which is not described herein. Other constructions and operations of refrigeration equipment according to embodiments of the present invention are known to those of ordinary skill in the art and will not be described in detail herein.

In the description of the present 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", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and to simplify the description, and do not indicate or imply that the device or element being referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present invention.

Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present invention, the meaning of "a plurality" is two or more, unless explicitly defined otherwise.

In the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.

In the present invention, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.

In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.

While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: many changes, modifications, substitutions and variations may be made to the embodiments without departing from the spirit and principles of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A discharge check valve for a compressor, the discharge check valve comprising:

The valve housing assembly comprises a valve housing and an exhaust pipe, the valve housing is provided with an air outlet, the air inlet end of the exhaust pipe is inserted and matched with the air outlet, the cross section area of the air inlet end is S1, and the compressor is suitable for unidirectional exhaust through the air outlet end of the exhaust pipe;

a valve core assembly which is arranged in the valve shell and comprises a valve core movable between an open position and a closed position, wherein an exhaust hole is formed on the valve core assembly, an exhaust channel communicated between the exhaust hole and the air outlet is formed between the valve core and the valve shell, when the valve core moves to the open position, the air in the valve core assembly can enter the exhaust channel from the exhaust hole and flow to the air inlet end,

when the valve core moves to the opening position, the nearest distance between the valve core and the valve shell is d2, the area of the minimum overflow surface of the exhaust passage is S2, wherein the ratio of S1 to d2 is 8-25, and/or the ratio of S2 to S1 is 1.2-5.

2. The discharge check valve for a compressor according to claim 1, wherein the valve body includes a cylindrical section coaxially disposed with the air outlet, the valve body is movable in an axial direction of the cylindrical section toward a direction approaching the air outlet to reach the open position, a shaft end of the cylindrical section toward the air outlet is a free end, and a shortest connecting line between an edge of the free end and the air outlet is the shortest distance d2 when the valve body is moved to the open position.

3. The discharge check valve for a compressor of claim 2, wherein the cross-section of the inlet end and the cross-section of the cylindrical section are both circular, and the minimum flow passage surface of the discharge passage is configured to: the axis of the cylindrical section is taken as a central line, the shortest connecting line is taken as a bus, the cross section of the air outlet is taken as a lower bottom, and the cross section of the free end is taken as the side surface of the truncated cone with an upper bottom.

4. The discharge check valve for a compressor according to claim 2, wherein the valve housing is formed as a revolution body with a center line of the gas outlet as a revolution axis.

5. The discharge check valve for a compressor according to claim 1, wherein the discharge holes are at least one, and a total flow area of all the discharge holes is S3, wherein a ratio of S3 to S2 is 0.3 to 0.8, and/or a ratio of S3 to S1 is 1 to 2, and/or a ratio of S3 to d2 is 12 to 30.

6. The discharge check valve for a compressor of claim 5, wherein the valve core assembly includes a valve inner housing having a central hole therein, the valve core includes a cylindrical section and a stopper section, the cylindrical section is disposed through the central hole, the stopper section is disposed in the valve inner housing and connected to an inner end of the cylindrical section to restrict the inner end of the cylindrical section from coming out of the central hole, and the discharge holes are plural and distributed on the valve inner housing in a circumferential direction of the cylindrical section.

7. The discharge check valve for a compressor according to claim 1, wherein a closest distance between the discharge hole and the valve housing is d3, wherein a ratio of S1 to d3 is 8 to 25, and/or a ratio of d2 to d3 is 0.7 to 1.5.

8. The discharge check valve for a compressor of claim 1, wherein the valve core assembly defines an inner cavity, the valve core assembly further has an air inlet hole thereon, the air inlet hole and the air outlet hole are both in communication with the inner cavity, the valve core is used for controlling the opening and closing of the air inlet hole, the air inlet hole has an over-flow area of S4, the air outlet hole has at least one air outlet hole, and the total over-flow area of all the air outlet holes is S3, wherein the ratio of S4 to S3 is 0.8-2.

9. The discharge check valve for a compressor of claim 8, wherein the valve cartridge assembly includes an inner valve housing and a valve seat defining the inner chamber therebetween, the air intake hole is formed on the valve seat, the air discharge hole is formed on the inner valve housing, and the valve cartridge is penetrated through the inner valve housing to reciprocate in a direction away from and toward the air intake hole.

10. The discharge check valve for a compressor of claim 9, wherein the valve outer housing cooperates with the valve seat to define a receiving chamber therebetween, the valve inner housing being disposed within the receiving chamber.

11. A discharge check valve for a compressor according to any one of claims 1-10, wherein S1 is 85mm ² -105mm ² D2 is 5.5mm to 6.5mm and S2 is 230mm ² -250mm ² 。

12. A compressor, comprising: the compressor comprises a shell component, a driving component, a pump body component and an exhaust one-way valve, wherein the driving component is connected with the pump body component and is arranged in the shell component, the exhaust one-way valve is arranged in the shell component and is used for the compressor according to any one of claims 1-11, and the exhaust pipe penetrates through the shell component.