Screw compressor

Abstract

The utility model discloses a screw compressor which comprises a screw compressor body provided with an air inlet end and an air outlet end, and further comprises an air inlet pipe arranged above the screw compressor body and communicated with the air inlet end, an air outlet pipe arranged above the screw compressor body and communicated with the air outlet end, and an air outlet pipe arranged above the screw compressor body and communicated with the air outlet end, the valve seat is arranged on the air inlet pipe and is used for mounting a pressure regulating element; the pressure regulating element comprises a valve plate and an elastic piece, and the valve plate is attached to the pressure regulating hole and connected with the elastic piece. According to the screw compressor provided by the utility model, through the arrangement of the pressure regulating element, the valve plate is in an elastic state, namely, the opening internal and external pressure difference of the valve plate is only 20kpa, when a unit works, after the compressor conveys air at the air inlet end to the high-pressure end, negative pressure is generated at the air inlet end, and as long as the absolute pressure of the air inlet end is below 80kpa, the valve plate can be in an elastic state under the action of atmospheric pressure. And the air inlet end is communicated with the atmosphere for air compensation, so that the pressure ratio of the compressor is reduced, and the internal structure of the compressor is protected.

Description

Technical Field

[0001] The utility model relates to the technical field of screw compressors, and particularly relates to a screw compressor. Background Art

[0002] A screw compressor is composed of a pair of parallel and meshing male and female screws, and is one of the most widely used rotary compressors. It can be divided into single-screw and double-screw types. Usually, the screw compressor refers to the double-screw compressor. The screw compressor can also be dry or wet. The so-called dry type means that no liquid is sprayed into the working chamber, and the compressed gas will not be polluted. The wet type means that lubricating oil or other liquids are sprayed into the working chamber to cool the compressed gas, improve the seal, and can lubricate the male and female rotors and bearings to achieve self-transmission. Then, through a high-precision filter, the oil or other liquid impurities in the compressed air are removed to obtain higher-quality compressed gas.

[0003] As shown in the attached Figure 9 description, it is a partial structural state diagram of the intake pipe connected to the intake port of the prior art screw compressor. When it is in the unloaded state, the intake valve disc 1-2 in the intake pipe 1-1 is in the closed state, and air cannot enter the main engine from the intake port. However, the screw compressor is a compressor that forcibly transports gas, and it will forcibly transport the air in the closed volume of the intake port to the exhaust port end below the main body. However, due to the small volume of the intake end and the closed state of the intake valve disc 1-2, external air cannot be compensated, and the intake end will be pumped into a vacuum state, sometimes even below 10 kPa;

[0004] At this time, the compressor is in the unloaded state. Because the exhaust end is connected to the air storage tank, there will be a pressure of about 400 kPa, resulting in a very large pressure ratio in the compression chamber, and even the pressure ratio will reach 40. The powerful pressure ratio will cause great damage to the inner surface of the main engine, and it is easy to cause the surface coating of other components such as the internal screw to be eroded, seriously reducing the actual service life of the compressor;

[0005] And in its normal loaded state, the intake valve disc 1-2 is in the open state, the intake port is in communication with the atmosphere, the pressure is about 100 kPa, and the pressure at the exhaust port end is about 800 kPa. At this time, the pressure ratio is only 8, the main engine consumes a large amount of power, but the pressure ratio is small, and the damage to the surface of the main engine is very small. Therefore, the pressure ratio in the unloaded state is larger than that in the loaded state. For this reason, a screw compressor is proposed. Summary of the Utility Model

[0006] Based on this, in view of the above technical problems, it is necessary to provide a screw compressor, which is provided with a pressure regulating element in the intake pipe to automatically open according to the action of the internal and external pressure difference during the unloaded state of the screw compressor to achieve air compensation, reduce the internal pressure ratio, and realize the protection of the compressor.

[0007] To solve the above technical problems, the present utility model adopts the following technical solutions:

[0008] A screw compressor, including a screw compressor body, which has an air inlet end and an air outlet end, and further includes:

[0009] An air inlet pipe, which is arranged above the screw compressor body and is communicated with the air inlet end;

[0010] A valve seat, which is arranged on the air inlet pipe for the installation of a pressure regulating element;

[0011] The pressure regulating element includes a valve plate and an elastic member, the valve plate is arranged in a fitting manner with a pressure regulating hole and is connected with the elastic member;

[0012] Wherein, the pressure regulating hole is arranged inside the valve seat, and under the action of the internal and external pressure difference, the valve plate can be tightly attached to or away from the pressure regulating hole, so as to reduce the high compression ratio inside the screw compressor body.

[0013] Further, the elastic member is respectively connected with the valve plate and the valve seat, and under the action of the elastic member, the valve plate is tightly attached to the pressure regulating hole in the natural state to form a blockage of the air inlet pipe.

[0014] Further, the elastic member includes an elastic part and a supporting part which are connected with each other, and the outer ends of the elastic part and the supporting part are respectively connected with the corresponding valve plate and valve seat.

[0015] Further, the valve plate is arranged below the pressure regulating hole.

[0016] Further, one end of the elastic part is connected to the bottom wall of the valve plate, and the supporting part is fixed to the bottom of the side wall of the valve seat and is connected with the upper elastic part.

[0017] Further, one end of the elastic part is connected to the top of the valve plate, and the supporting part is fixed to the top of the side wall of the valve seat and is connected with the lower elastic part.

[0018] Further, the supporting part is a supporting seat.

[0019] Further, the elastic part is a spring.

[0020] Further, the air inlet pipe includes an outer pipe and an inner pipe, wherein the outer pipe is connected with an external atmosphere pipeline, and the inner pipe is connected with the screw compressor body through the air inlet end;

[0021] Both the top and the bottom of the valve seat have openings, and the outer pipe, the valve seat and the inner pipe are sequentially connected and jointly used for the transportation of the external atmosphere towards the inside of the screw compressor.

[0022] Further, the outer diameter of the valve plate is larger than the inner diameter of the pressure regulating hole and smaller than the inner diameter of the valve seat.

[0023] Compared with the prior art, the utility model has the following beneficial effects:

[0024] For the screw compressor provided by the utility model, through the setting of the pressure regulating element, the valve plate is in an elastic state, that is, the internal and external pressure difference for the valve plate to open is only 20 kPa. When the unit is working, after the compressor conveys the air at the intake end to the high-pressure end, a negative pressure is generated at the intake end. As long as the absolute pressure at the intake end is below 80 kPa, the valve plate will automatically open under the action of the atmospheric pressure, making the intake end communicate with the atmosphere for gas compensation, so as to reduce the compression ratio of the compressor and protect its internal structure;

[0025] When the machine stops, the compressor stops delivering gas, and the gas at the high-pressure end returns to the intake end. Under the elastic reset action of the spring, the valve plate will also automatically close to prevent the high-pressure gas from spraying out from the intake end;

[0026] Therefore, no matter whether the compressor is in a light-load, heavy-load or shutdown state, a high vacuum state will never occur at the intake end. In the light-load state, the compression ratio of the compression chamber of the compressor is only 1-2, and in the heavy-load state, it is only 8-10. Therefore, the situation of high compression ratio is avoided, and the damage to the rotor caused by the high compression ratio is greatly reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 is a schematic structural diagram of the screw compressor provided by the utility model;

[0028] Figure 2 is a schematic disassembly structural diagram of the screw compressor provided by the utility model;

[0029] Figure 3 is a schematic cross-sectional structural diagram of the intake pipe of the screw compressor provided by the utility model;

[0030] Figure 4 is a partial structural schematic diagram of the pressure regulating element in the first state of Embodiment 1 of the screw compressor provided by the utility model;

[0031] Figure 5 is a schematic cross-sectional structural diagram of the pressure regulating element in the first state of Embodiment 1 of the screw compressor provided by the utility model;

[0032] Figure 6 is a partial structural schematic diagram of the pressure regulating element in Embodiment 2 of the screw compressor provided by the utility model;

[0033] Figure 7 is a schematic structural diagram of the first form of the pressure regulating element in Embodiment 3 of the screw compressor provided by the utility model;

[0034] Figure 8 is a schematic structural diagram of the second form of the pressure regulating element in Embodiment 3 of the screw compressor provided by the utility model;

[0035] Figure 9 It is a schematic structural diagram of the existing screw compressor described in the background art.

[0036] The markings in the figure are explained as follows:

[0037] Screw compressor body 1, intake end 11, exhaust end 12, intake pipe 13;

[0038] Outer pipe 130, inner pipe 131,

[0039] Pressure regulating element 2, valve seat 21, valve plate 22, elastic member 23, pressure regulating hole 24,

[0040] Opening 210;

[0041] Elastic part 230, support part 231, support seat 232. Detailed implementation manners

[0042] In order to enable those skilled in the art to better understand the solution of the present invention, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0043] As in the background art, as shown in the attached drawings of the specification Figure 9 Shown, it is a partial structural state diagram of the intake pipe connected to the intake port on the existing screw compressor. When it is in the unloaded state, the intake valve plate 1-2 in the intake pipe 1-1 is in the closed state, and air cannot enter the main engine from the intake port. However, the screw compressor is a type of compressor that forcibly delivers gas, and it will forcibly deliver the air in the closed volume of the intake port to the exhaust port end below the main body. However, due to the small volume of the intake end and the closed state of the intake valve plate 1-2, external air cannot be compensated, and the intake end will be pumped into a vacuum state, sometimes even below 10 kPa;

[0044] At this time, the compressor is in the unloaded state. Because the exhaust end is connected to the air storage tank, there will be a pressure of about 400 kPa, resulting in a very large pressure ratio in the compression chamber, and even the pressure ratio will reach 40. The strong pressure ratio will cause very great damage to the inner surface of the main engine, easily causing the surface coating of other components such as the internal screw to be eroded, and seriously reducing the actual service life of the compressor.

[0045] To solve this technical problem, the present invention provides a screw compressor, which is applied to a screw compressor.

[0046] Specifically, please refer to Figures 1-9 The screw compressor specifically includes a screw compressor body 1, which has an air inlet end 11 and an air outlet end 12, and further includes:

[0047] An air inlet pipe 13, which is arranged above the screw compressor body 1 and communicated with the air inlet end 11;

[0048] A valve seat 21, which is arranged on the air inlet pipe 13 for installing a pressure regulating element 2;

[0049] The pressure regulating element 2 includes a valve plate 22 and an elastic element 23. The valve plate 22 is arranged in a fitting manner with a pressure regulating hole 24 and connected with the elastic element 23;

[0050] Wherein, the pressure regulating hole 24 is arranged inside the valve seat 21. Under the action of the internal and external pressure difference, the valve plate 22 can be tightly attached to or away from the pressure regulating hole 24, so as to reduce the high compression ratio inside the screw compressor body 1.

[0051] For the screw compressor provided by the present utility model, through the arrangement of the pressure regulating element 2, the valve plate 22 is in an elastic state, that is, the internal and external pressure difference for the opening of the valve plate 22 only needs 20 kPa. When the unit is working, after the compressor conveys the air at the air inlet end 11 to the high-pressure end of the air outlet end 12, a negative pressure is generated at the air inlet end 11. As long as the absolute pressure at the air inlet end 11 is below 80 kPa, the valve plate 22 will automatically open under the action of the atmospheric pressure, so that the air inlet end 11 is communicated with the atmosphere for gas compensation, thereby reducing the compression ratio of the compressor and realizing the protection of its internal structure;

[0052] When the machine stops, the compressor stops delivering gas, and the high-pressure gas at the air outlet end 12 returns to the air inlet end 11. Under the elastic reset action of the spring, the valve plate 22 will also automatically close to prevent the high-pressure gas from spraying out from the air inlet end;

[0053] Therefore, no matter whether the compressor is in a light load, heavy load or shutdown state, a high vacuum state will never be generated at the air inlet end. In the light load state, the compression ratio of the compression chamber of the compressor is only 1-2, and in the heavy load state, it is only 8-10. Therefore, the situation of generating a high compression ratio is avoided, and the damage to the rotor caused by the high compression ratio is greatly reduced.

[0054] In order to enable those skilled in the art to better understand the solution of the present utility model, the technical solutions in the embodiments of the present utility model will be clearly and completely described below with reference to the accompanying drawings.

[0055] It should be noted that, without conflict, the embodiments in the present utility model and the features and technical solutions in the embodiments can be combined with each other.

[0056] It should be noted that similar reference numerals and letters indicate similar items in the following drawings. Therefore, once an item is defined in one drawing, it does not need to be further defined and explained in the subsequent drawings.

[0057] Please refer to Figures 1-5 As shown, a screw compressor includes a screw compressor body 1, which has an air inlet end 11 and an air outlet end 12. It also includes: an air inlet pipe 13, which is arranged above the screw compressor body 1 and communicated with the air inlet end 11;

[0058] A valve seat 21, which is arranged on the air inlet pipe 13 for installing a pressure regulating element 2;

[0059] The pressure regulating element 2 includes a valve plate 22 and an elastic member 23. The valve plate 22 is arranged in fit with a pressure regulating hole 24 and connected with the elastic member 23. Among them, the pressure regulating hole 24 is arranged inside the valve seat 21. Under the action of the internal and external pressure difference, the valve plate 22 can be close to or away from the pressure regulating hole 24, which is used to reduce the high compression ratio inside the screw compressor body 1.

[0060] Please refer to Figure 3 、 4 As shown in Figures 5, the elastic member 23 is respectively connected with the valve plate 22 and the valve seat 21. Under the action of the elastic member 23, the valve plate 22 is tightly attached to the pressure regulating hole 24 in the natural state to form a blockage of the air inlet pipe 13;

[0061] The elastic member 23 includes an elastic part 230 and a support part 231 which are connected with each other. The outer ends of the elastic part 230 and the support part 231 are respectively connected with the corresponding valve plate 22 and valve seat 21. One end of the elastic part 230 is connected to the bottom wall of the valve plate 22. The support part 231 is fixed to the bottom of the side wall of the valve seat 21 and connected with the upper elastic part 230. The support part 231 is a support seat 232, and the elastic part 230 is a spring;

[0062] The valve plate 22 is arranged below the pressure regulating hole 24, and the support part 231 is fixed to the bottom of the side wall of the valve seat 21;

[0063] As Figure 4 shown, in this embodiment, the valve plate 22 is located below the pressure regulating hole 24. Under the action of the elastic part 230 at the bottom, the valve plate 22 is in contact with the surface of the pressure regulating hole 24 in the natural state. The pressure regulating hole 24 under the contact action will form a blockage of the air inside the valve seat 21, and the air in the air inlet pipe 13 cannot be input into the inside of the screw compressor body 1 without external force. Similarly, the air in the screw compressor body 1 cannot be discharged into the inside of the air inlet pipe 13;

[0064] However, due to the fact that there is a certain pressure difference between the inside and outside of the valve plate 22 during the actual operation of the screw compressor body 1, and the elastic force of the spring of the elastic part 230 itself is also limited. Therefore, the condition for the spring set in this embodiment to meet the downward compression is that the pressure difference between the inside and outside of the valve plate 22 reaches 20 kPa;

[0065] After meeting the requirements for the opening of the valve plate 22 above, when the screw compressor body 1 operates, after the compressor delivers the air in the intake end 11 to the exhaust end (high-pressure end), a negative pressure will be generated in the intake end 11. As long as the absolute pressure in the intake end 11 is below 80 kPa, the valve plate 22 will move downward under the action of atmospheric pressure, causing the spring to undergo compressive deformation, so as to realize the automatic opening of the valve plate 22, so that the intake end 11 communicates with the external atmosphere through the intake pipe 13, so as to reduce the pressure ratio inside the screw compressor body 1;

[0066] When the machine stops, the screw compressor body 1 will stop delivering gas, and the gas at the exhaust end 12 (high-pressure end) will return to the intake end 11. At this time, under the action of the spring, the valve plate 22 will move upward and abut against the pressure regulating hole 24 to automatically close, preventing the high-pressure gas from spraying out from the intake end 11.

[0067] Therefore, when using the structure of the intake check valve in this embodiment, regardless of whether it is in the light load, heavy load, or shutdown state, the intake end 11 will never produce a high vacuum state. In the light load state, the pressure ratio of the compression chamber of the compressor is only 1-2, and in the heavy load state, it is only 8-10. Compared with the valve plate in the fixed state inside the traditional screw compressor body 1, it can effectively avoid the situation of generating a high compression ratio, thereby greatly reducing the damage to the rotor inside the screw compressor body 1 caused by the high compression ratio.

[0068] The difference between this embodiment and Embodiment 1 is that the support portion 231 in Embodiment 1 is provided at the bottom wall of the side wall of the valve seat 21, while the support portion 231 in this embodiment is fixed to the top of the side wall of the valve seat 21. Specifically as follows: One end of the elastic portion 230 is connected to the top of the valve plate 22, and the support portion 231 is fixed to the top of the side wall of the valve seat 21 and is connected to the elastic portion 230 below. The support portion 231 is a support seat 232, and the elastic portion 230 is a spring;

[0069] As Figure 1 、 2 and Figure 6 shown, the valve plate 22 in this embodiment is arranged below the pressure regulating hole 24, and the support portion 231 is fixed to the top of the side wall of the valve seat 21;

[0070] The principle is the same as that in Embodiment 1. After the pressure difference inside and outside the valve plate 22 reaches a certain value, the valve plate 22 moves downward under the negative pressure action of the intake end 11, releasing the blockage of the pressure regulating hole 24, so that the external gas can pass through the intake pipe 13 into the valve seat 21 and finally compensate into the screw compressor body 1, so as to reduce the compression ratio inside the screw compressor body 1 and meet the functional requirements for protecting the internal rotor;

[0071] The difference between the spring in this embodiment and that in Embodiment 1 is that when the valve plate 22 in Embodiment 1 is opened, the valve plate 22 is in a downward movement state, and the spring connected to it will be compressed. While in this embodiment, when the valve plate 22 is opened, although the valve plate 22 is also in a downward movement state, the spring connected to it is in a tensile state;

[0072] Therefore, when used according to the actual working conditions, how to make the elastic coefficient of the spring meet the requirement that the valve plate 22 can be automatically opened and closed under a certain absolute pressure. This requires the operator to select the corresponding type of spring according to the pressure difference in the required opening state of the valve plate 22 during the actual application process. For example, if a larger pressure difference is required for the spring to be compressed or stretched to open the valve plate 22, then the elastic coefficient of the required spring needs to be higher. On the contrary, a spring with a lower elastic coefficient needs to be selected, which will not be elaborated too much in this embodiment.

[0073] This embodiment further optimizes the screw compressors in Embodiment 1 and Embodiment 2: The number of the springs is several:

[0074] Such as Figure 1 、 2 、7 and Figure 8 As shown in the figure, the springs in Embodiment 1 and Embodiment 2 are both single springs used to connect the valve plate 22 and the valve seat 21. Therefore, when a larger pressure difference is required to open the valve plate 22, the requirement for the elastic coefficient of the spring itself is relatively high. The spring needs to resist a larger pressure and still maintain the sealing of the valve plate 22. Therefore, the preparation process and cost of such a spring with a high elastic coefficient are also higher. In this embodiment, multiple springs with a lower elastic coefficient can be centrally arranged to comprehensively achieve the elastic sealing with a high elastic coefficient, specifically as follows:

[0075] Such as Figure 7 As shown in the figure, the setting position of the valve plate 22 at this time corresponds to the position of the valve plate 22 in Embodiment 1. The valve plate 22 seals below the pressure regulating hole 24, and the spring is also located below the pressure regulating hole 24. At this time, 3 groups of springs are arranged equidistantly in a ring at the bottom of the valve plate 22, and all 3 groups of springs are connected to the lower valve seat 21 below. It is required that the compressive value achieved by the 3 groups of springs together is the same as that achieved by a single spring in Embodiment 1, which can not only reduce the preparation difficulty and cost of the spring, but also make the force between the valve plate 22 and the valve seat 21 more uniform through multiple springs arranged equidistantly in a ring, which is more conducive to its opening and closing;

[0076] Such as Figure 8As shown, the setting position of the valve plate 22 at this time corresponds to the position of the valve plate 22 in Embodiment 2. The valve plate 22 blocks below the pressure regulating hole 24, and the spring is arranged above the pressure regulating hole 24. At this time, 3 groups of springs are arranged annularly and equidistantly at the top of the valve plate 22. Neither the stretched state nor the natural state of the springs will form a movement obstacle to the pressure regulating hole 24. The 3 groups of springs are all connected to the upper valve seat 21. Similarly, the compressive value achieved by the 3 groups of springs together is equal to the compressive value achieved by a single spring in Embodiment 2. Specifically, the setting method of the spring position and the number of springs arranged can be adaptively adjusted according to the actual application.

[0077] As Figure 2 and Figure 3 shown, further optimizations are made to Embodiment 1, Embodiment 2, and Embodiment 3: The air inlet pipe 13 includes an outer pipe 130 and an inner pipe 131. Among them, the outer pipe 130 is connected to the external atmosphere pipeline, and the inner pipe 131 is connected to the screw compressor body 1 through the air inlet end 11;

[0078] Both the top and bottom of the valve seat 21 have openings 210. The outer pipe 130, the valve seat 21, and the inner pipe 131 are connected in sequence and are jointly used for the delivery of the external atmosphere into the screw compressor body 1;

[0079] When the valve plate 22 is not attached to the surface of the pressure regulating hole 24, the outer pipe 130, the valve seat 21, the inner pipe 131, and the screw compressor body 1 are in a mutually connected state. When the valve plate 22 is pressed tightly against the surface of the pressure regulating hole 24, the outer pipe 130 and the inner pipe 131 are in a separated state;

[0080] During the actual installation process, the valve seat 21 is arranged between the inner pipe 131 and the outer pipe 130. Sealing rubber rings are embedded at the top and bottom of the valve seat 21 corresponding to the outer pipe 130 and the inner pipe 131, thereby enhancing the sealing effect of the contact surface. Then, the inner pipe 131 and the outer pipe 130 are locked by screws to complete the fastening connection with the valve seat 21;

[0081] The outer diameter of the valve plate 22 is larger than the inner diameter of the pressure regulating hole 24 and smaller than the inner diameter of the valve seat 21.

[0082] Whether in Embodiment 1 or Embodiment 2, there are gaps between the support seats 231 connected to the top side wall and the bottom side wall of the side wall of the valve seat 21 and the opening 210 of the valve seat 21, and the air on both sides of the valve plate 22 can flow through these gaps for interaction;

[0083] For example, the process of the air in the outer pipe 130 being input into the screw compressor body 1 is as follows: The gas in the outer pipe 130 is input into the valve seat 21. The air input into the valve seat 21 is input into the inner pipe 131 through the pressure regulating hole 24, and the gas in the inner pipe 131 is then input into the interior of the screw compressor body 1 through the air inlet end 11.

[0084] In the present utility model, unless otherwise clearly defined and limited, terms such as "installation", "connection", "linkage", "fixation", etc. shall be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral one; it may be a mechanical connection, an electrical connection, or communication with each other; it may be directly connected, or indirectly connected through an intermediate medium, and it may be the internal connection of two components or the interaction relationship between two components, unless otherwise clearly defined. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific circumstances.

[0085] Obviously, the embodiments described above are only part of the embodiments of the present utility model, rather than all embodiments. The accompanying drawings show the preferred embodiments of the present utility model, but do not limit the patent scope of the present utility model. The present utility model can be implemented in many different forms. On the contrary, the purpose of providing these embodiments is to make the understanding of the disclosed content of the present utility model more thorough and comprehensive. Although the present utility model has been described in detail with reference to the foregoing embodiments, for those skilled in the art, they can still modify the technical solutions described in the foregoing specific embodiments, or perform equivalent replacements for some of the technical features. Any equivalent structure directly or indirectly using the content of the specification and drawings of the present utility model in other related technical fields shall be within the scope of the patent protection of the present utility model by the same token.

Claims

1. A screw compressor, comprising a screw compressor body (1), the screw compressor body (1) having an air inlet end (11) and an air outlet end (12), characterized in that, Further included are: An intake pipe (13) which is arranged above the screw compressor body (1) and communicated with the intake end (11); A valve seat (21) which is arranged on the intake pipe (13) for the installation of a pressure regulating element (2); The pressure regulating element (2) includes a valve plate (22) and an elastic member (23), and the valve plate (22) is arranged in a manner of fitting the pressure regulating hole (24) and connected with the elastic member (23); Wherein, the pressure regulating hole (24) is arranged inside the valve seat (21), and under the action of the internal and external pressure difference, the valve plate (22) can be close to or away from the pressure regulating hole (24) to reduce the high compression ratio inside the screw compressor body (1).

2. The screw compressor according to claim 1, wherein The elastic member (23) is respectively connected with the valve plate (22) and the valve seat (21), and under the action of the elastic member (23), the valve plate (22) is tightly attached to the pressure regulating hole (24) in the natural state to form a seal for the intake pipe (13).

3. The screw compressor according to claim 2, wherein The elastic member (23) includes an elastic part (230) and a support part (231) which are connected with each other, and the outer ends of the elastic part (230) and the support part (231) are respectively connected with the corresponding valve plate (22) and valve seat (21).

4. The screw compressor according to claim 3, wherein The valve plate (22) is arranged below the pressure regulating hole (24).

5. The screw compressor according to claim 4, wherein, One end of the elastic part (230) is connected to the bottom wall of the valve plate (22), and the support part (231) is fixed to the bottom of the side wall of the valve seat (21) and connected with the upper elastic part (230).

6. The screw compressor according to claim 4, wherein, One end of the elastic part (230) is connected to the top of the valve plate (22), and the support part (231) is fixed to the top of the side wall of the valve seat (21) and connected with the lower elastic part (230).

7. The screw compressor according to claim 3, characterized in that The support part (231) is a support seat (232).

8. The screw compressor according to claim 3, wherein, The elastic part (230) is a spring.

9. The screw compressor according to claim 1, characterized in that, The intake pipe (13) includes an outer pipe (130) and an inner pipe (131), wherein, the outer pipe (130) is connected with an external atmosphere pipeline, and the inner pipe (131) is connected with the screw compressor body (1) through the intake end (11); Both the top and the bottom of the valve seat (21) have openings (210), and the outer pipe (130), the valve seat (21) and the inner pipe (131) are sequentially connected and jointly used for the delivery of the external atmosphere into the screw compressor body (1).

10. The screw compressor according to any one of claims 1-9, characterized in that, The outer diameter of the valve plate (22) is larger than the inner diameter of the pressure regulating hole (24) and smaller than the inner diameter of the valve seat (21).

Images