Compressor zero-pressure-difference suction check valve

Abstract

The utility model provides a compressor zero pressure difference suction check valve relates to compressor valve technical field, and valve plate assembly is in valve body and cooperates sealing pad sealed suction passage, reset spring acts on valve plate and provides the pre -tightening force of making it reset, still include drive assembly and guide air pipeline, drive assembly assembly is in valve body upper end, and drive assembly includes cylinder liner, drive piston and push rod, cylinder liner is fixed with valve body, drive piston sets up in the cylinder liner inside to form cylinder cavity with the slidable, push rod upper end is connected in drive piston, and lower end acts on the upper end surface of valve plate, guide air pipeline is connected cylinder cavity with the exhaust end of compressor, is used for introducing the high pressure exhaust of compressor into cylinder cavity as drive power source, when compressor operation, high pressure exhaust enters cylinder cavity through guide air pipeline, drives drive piston and drives push rod down, initiatively overcomes the pre -tightening resistance of reset spring and drives valve plate to open, realizes zero pressure difference suction conduction.

Description

Technical Field

[0001] This utility model relates to the field of compressor valve technology, and more specifically, to a compressor zero differential pressure suction check valve, which is applicable to refrigeration and process gas compressors. Background Technology

[0002] During compressor operation, the suction check valve is a core component in the suction circuit. Its main function is to prevent high-pressure side gas (helium, nitrogen, etc.) from flowing back to the suction side after the compressor stops or its operating conditions change, thus avoiding problems such as compressor reversal, gas cross-contamination, and reduced unit efficiency. Currently, most mainstream suction check valves in the industry adopt a spring-reset structure. This relies on the pressure difference between the compressor's suction chamber and the external suction pipeline to overcome the spring preload, pushing the valve plate open and opening the suction passage. When the compressor stops, the spring force pushes the valve plate closed, achieving a seal.

[0003] Traditional spring-return suction check valves suffer from numerous insurmountable defects in practical applications, becoming a key bottleneck restricting compressor performance improvement. Firstly, traditional spring-return suction check valves have a fixed opening differential pressure threshold. During compressor startup, low-load, low-frequency operation, and when suction pressure fluctuations are small, the suction pressure differential cannot overcome the spring resistance, resulting in delayed or insufficient opening of the check valve. This leads to insufficient suction volume, reduced volumetric efficiency, and a significant decrease in unit energy efficiency. Secondly, in system design, the conventional approach to reduce the opening differential pressure of the suction check valve is to decrease the spring stiffness. However, this results in insufficient valve closing force, decreased sealing reliability, and a tendency for backflow leakage under high back pressure conditions, failing to balance low-resistance opening and high sealing performance. Thirdly, suction check valves relying on differential pressure opening have poor adaptability. Under complex conditions such as low-temperature refrigeration, variable frequency or variable load operation, and parallel operation of multiple units, insufficient suction flow and differential pressure make it difficult to guarantee unit operational stability and energy efficiency.

[0004] In summary, the existing spring-reset suction check valve has structural limitations that rely on pressure difference for passive opening, preventing it from achieving zero pressure difference suction. This restricts the improvement of compressor energy efficiency and operational stability under all operating conditions. There is an urgent need to design a new suction check valve structure that can be actively driven, overcome spring resistance, and open with zero pressure difference. Utility Model Content

[0005] To address the structural limitations of existing spring-return suction check valves that rely on differential pressure for passive opening, thus preventing them from achieving zero-differential-pressure suction, this invention provides a compressor zero-differential-pressure suction check valve. This invention primarily utilizes the compressor's own discharge pressure as the driving force, actively driving the valve plate to open via a cylinder piston. This overcomes spring resistance and solves the problems of delayed start-up, insufficient suction under low loads, and poor adaptability of compressor suction check valves, significantly improving the compressor's energy efficiency under all operating conditions.

[0006] The technical means adopted in this utility model are as follows: A compressor zero-differential-pressure suction check valve includes a valve body, a valve plate, a return spring, a sealing gasket, and a guide and limiting assembly; the valve plate is assembled in the valve body and cooperates with the sealing gasket to seal the suction passage, and the return spring acts on the valve plate and provides a preload force to reset it; It also includes a drive assembly and an air guide pipe; the drive assembly is assembled on the upper end of the valve body, and the drive assembly includes a cylinder liner, a drive piston, and a push rod. The cylinder liner is fixed to the valve body, and the drive piston is slidably disposed inside the cylinder liner to form a cylinder cavity. The upper end of the push rod is connected to the drive piston, and the lower end acts on the upper end face of the valve plate; the air guide pipe connects the cylinder cavity and the exhaust end of the compressor, and is used to introduce the high-pressure exhaust of the compressor into the cylinder cavity as a drive power source; When the compressor is running, high-pressure exhaust gas enters the cylinder cavity through the air guide pipe, pushing the drive piston to drive the push rod downward, actively overcoming the preload resistance of the return spring and driving the valve plate to open, thus achieving zero-pressure differential intake conduction.

[0007] Furthermore, the drive assembly also includes a cylinder head, which is fixed to the upper end of the cylinder liner and together with the cylinder liner and the drive piston, forms the cylinder cavity; the air guide pipe is connected to the cylinder cavity through a first ferrule connector provided on the cylinder head.

[0008] Furthermore, a first solenoid valve is provided on the air guide pipe to control the opening and closing of the compressor exhaust end to the cylinder cavity; when the compressor is started, the first solenoid valve opens, and high-pressure exhaust enters the cylinder cavity to drive the valve plate to open.

[0009] Furthermore, it also includes a second solenoid valve and a release pipeline; one end of the release pipeline is connected to the cylinder cavity, and the other end is connected to the intake end of the valve body, and the second solenoid valve is disposed on the release pipeline; When the compressor stops, the first solenoid valve closes and the second solenoid valve opens. The pressure inside the cylinder cavity is released through the release pipeline, causing the valve plate to reset and close under the action of the return spring.

[0010] Furthermore, the release line is connected to the valve body via a second ferrule connector.

[0011] Furthermore, the first solenoid valve is a normally closed solenoid valve, and the second solenoid valve is a normally open solenoid valve.

[0012] Furthermore, a buffer wear-resistant pad is provided at the contact point between the push rod and the valve plate.

[0013] Furthermore, a sealing gasket is fitted on the outer side of the drive piston to achieve cylinder cavity sealing.

[0014] Compared with the prior art, the present invention has the following advantages: 1. Abandoning the traditional passive opening mode of differential pressure, it uses the compressor's own discharge pressure as the driving force, and actively drives the valve plate to open through the cylinder piston, overcoming spring resistance, solving industry pain points such as delayed start of compressor suction check valve, insufficient suction at low load, and poor adaptability to working conditions, and greatly improving the compressor's energy efficiency under all working conditions.

[0015] 2. It adopts a combination structure of return spring and active exhaust drive. The spring is only responsible for resetting the seal when the machine stops, and there is no need to consider the opening resistance. At the same time, the spring quickly resets the seal after the machine stops, eliminating backflow leakage and solving the structural contradiction of traditional valves where soft springs are prone to leakage and hard springs are difficult to open.

[0016] 3. The active drive opening method has no pressure difference loss and the suction passage is fully opened, which effectively improves the compressor's suction efficiency and reduces suction power consumption; it has a wide range of operating conditions and can be adapted to complex operating scenarios such as frequency conversion regulation, low temperature refrigeration, and parallel operation of multiple units, which significantly improves the unit's operating stability and energy saving, and extends the compressor's service life. Attached Figure Description

[0017] To more clearly illustrate the embodiments of this utility model or the technical solutions of the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the suction check valve structure according to an embodiment of the present utility model.

[0019] Figure 2 This is a schematic diagram of the air guide pipe connection in an embodiment of this utility model.

[0020] In the figure: 1-valve body; 2-guide and limit assembly; 3-valve plate; 4-reset spring; 5-sealing gasket; 6-push rod; 7-cylinder liner; 8-first ferrule connector; 9-drive piston; 10-fixing nut; 11-cylinder head; 12-second ferrule connector; 13-first solenoid valve; 14-second solenoid valve. Detailed Implementation

[0021] It should be noted that, where there is no conflict, the embodiments and features in the embodiments of this utility model can be combined with each other. The present utility model will now be described in detail with reference to the accompanying drawings and embodiments.

[0022] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit this utility model or its application or use. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this utility model.

[0023] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to the present invention. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0024] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0025] This utility model provides a zero-differential-pressure suction check valve for a compressor. For example... Figure 1-2 As shown, the valve includes a valve body 1, a valve plate 3, a return spring 4, a sealing gasket 5, and a guide limiting assembly 2. The sealing gasket 5 is installed on the valve plate 3 and is assembled inside the valve body 1. The return spring 4 is fitted onto the guide limiting assembly 2, which is assembled with the valve plate 3 and fixed to the valve body 1 with bolts. Under normal conditions, the preload force of the return spring 4 drives the valve plate 3 to adhere to the valve seat, achieving a seal in the intake passage.

[0026] A drive assembly is installed on the upper part of the valve body 1. The drive assembly includes a cylinder liner 7, a cylinder head 11, a drive piston 9, a push rod 6, and a fixing nut 10. The cylinder liner 7 is interference-fitted into the valve body 1. The drive piston 9 is assembled inside the cylinder liner 7. The drive piston 9 is fixedly connected to the push rod 6 by the fixing nut 10. The lower end of the push rod 6 abuts against the upper end face of the valve plate 3. The cylinder head 11 is provided on the upper part of the valve body 1. The cylinder liner 7, the drive piston 9, and the cylinder head 11 form a cylinder cavity. The air guide pipe is connected to the cylinder cavity through a first compression fitting 8 installed on the cylinder head 11.

[0027] The outer periphery of the drive piston 9 is nested with a high-temperature and wear-resistant rubber sealing ring to achieve complete sealing of the cylinder cavity and ensure stable drive pressure; the bottom end of the push rod 6 is directly opposite the center position of the valve plate 3 and is attached with a polyurethane buffer wear-resistant pad to avoid rigid contact wear and operating noise.

[0028] A first solenoid valve 13 is installed on the air guide pipe to control the opening and closing of the compressor exhaust end to the cylinder cavity; when the compressor is started, the first solenoid valve 13 opens, and the high-pressure exhaust enters the cylinder cavity to drive the valve plate 3 to open.

[0029] It also includes a second solenoid valve 14 and a release line; one end of the release line is connected to the cylinder cavity, and the other end is connected to the intake end of the valve body 1, and the second solenoid valve 14 is disposed on the release line. When the compressor stops, the first solenoid valve 13 closes and the second solenoid valve 14 opens. The pressure inside the cylinder cavity is quickly released through the release line, causing the valve plate 3 to reset and close under the action of the return spring 4. The release line is connected to the valve body 1 through the second compression fitting 12.

[0030] The first solenoid valve 13 is a normally closed solenoid valve, and the second solenoid valve 14 is a normally open solenoid valve.

[0031] In this embodiment, the reset spring 4 is a stainless steel spring, and the preload force is only sufficient to meet the shutdown sealing requirements.

[0032] When the equipment is running, the first solenoid valve 13 is open and the second solenoid valve 14 is closed. The high-pressure exhaust gas generated at the moment the compressor starts enters the cylinder cavity through the air guide pipe, the first solenoid valve 13, and the first compression fitting 8, pushing the drive piston 9 to drive the push rod 6 downward, actively pushing the valve plate 3 to compress the return spring 4. The valve plate 3 quickly disengages from the valve seat, the intake passage is opened, and there is no intake pressure loss, achieving zero pressure difference intake. During the continuous operation of the compressor, the exhaust pressure is maintained in the downward state of the drive piston 9, ensuring that the valve plate 3 is stably opened and the intake is smooth and lossless.

[0033] After the compressor stops, the first solenoid valve 13 is closed and the second solenoid valve 14 is opened. The gas inside the cylinder cavity is connected to the suction end of the check valve through the first ferrule 8, the air guide pipe, the second solenoid valve 14, and the second ferrule 12. The pressure in the cavity is balanced with the pressure in the suction pipe. Under the pre-tightening force of the return spring 4, the valve plate 3 quickly adheres to the valve seat, closing the suction passage and preventing high-pressure gas backflow and high-low pressure cross-flow, thus ensuring the stability of the unit during shutdown.

[0034] The above description is only a preferred embodiment of the present utility model, but the protection scope of the present utility model is not limited thereto. Any equivalent substitutions or changes made by those skilled in the art within the technical scope disclosed in the present utility model, based on the technical solution and concept of the present utility model, should be included within the protection scope of the present utility model.

Claims

1. A compressor zero-differential-pressure suction check valve, characterized in that, It includes a valve body, a valve plate, a return spring, a sealing gasket, and a guide and limiting assembly; the valve plate is assembled in the valve body and cooperates with the sealing gasket to seal the air intake passage; the return spring acts on the valve plate and provides a preload force to reset it. It also includes a drive assembly and an air guide pipe; the drive assembly is assembled on the upper end of the valve body, and the drive assembly includes a cylinder liner, a drive piston, and a push rod. The cylinder liner is fixed to the valve body, and the drive piston is slidably disposed inside the cylinder liner to form a cylinder cavity. The upper end of the push rod is connected to the drive piston, and the lower end acts on the upper end face of the valve plate; the air guide pipe connects the cylinder cavity and the exhaust end of the compressor, and is used to introduce the high-pressure exhaust of the compressor into the cylinder cavity as a drive power source; When the compressor is running, high-pressure exhaust gas enters the cylinder cavity through the air guide pipe, pushing the drive piston to drive the push rod downward, actively overcoming the preload resistance of the return spring and driving the valve plate to open, thus achieving zero-pressure differential intake conduction.

2. The compressor zero-differential suction check valve according to claim 1, characterized in that, The drive assembly also includes a cylinder head, which is fixed to the upper end of the cylinder liner and together with the cylinder liner and the drive piston, forms the cylinder cavity; the air guide pipe is connected to the cylinder cavity through a first ferrule connector provided on the cylinder head.

3. The compressor zero-differential suction check valve according to claim 1, characterized in that, A first solenoid valve is installed on the air guide pipe to control the opening and closing of the compressor exhaust end to the cylinder cavity; when the compressor is started, the first solenoid valve opens, and high-pressure exhaust enters the cylinder cavity to drive the valve plate to open.

4. A compressor zero-differential suction check valve according to claim 3, characterized in that, It also includes a second solenoid valve and a release line; one end of the release line is connected to the cylinder cavity, and the other end is connected to the intake end of the valve body, and the second solenoid valve is disposed on the release line; When the compressor stops, the first solenoid valve closes and the second solenoid valve opens. The pressure inside the cylinder cavity is released through the release pipeline, causing the valve plate to reset and close under the action of the return spring.

5. A compressor zero-differential suction check valve according to claim 4, characterized in that, The release line is connected to the valve body via a second compression fitting.

6. A compressor zero-differential suction check valve according to claim 4, characterized in that, The first solenoid valve is a normally closed solenoid valve, and the second solenoid valve is a normally open solenoid valve.

7. A compressor zero-differential suction check valve according to claim 1, characterized in that, A cushioning and wear-resistant pad is provided at the contact point between the push rod and the valve plate.

8. A compressor zero-differential suction check valve according to claim 1, characterized in that, A sealing gasket is fitted on the outside of the drive piston to achieve cylinder cavity sealing.

Images