Overflow control device of booster compressor

Abstract

The utility model provides an overflow control device of a booster compressor, which comprises a combined cylinder body, a variable-diameter piston arranged in the combined cylinder body, a gas chamber arranged above the variable-diameter piston, a gas inlet and a gas outlet connected with the gas chamber, a hydraulic oil chamber arranged below the variable-diameter piston, and a reciprocating pump connected with the hydraulic oil chamber through a connecting pipeline. The reciprocating pump cavity, the hydraulic part of the combined cylinder body and the connecting pipeline jointly form a closed hydraulic part, the closed hydraulic part is connected with a pressure control valve, the pressure control valve comprises an oil supply port, an oil outlet and a pneumatic control port, the oil supply port is connected with the closed hydraulic part through a pipeline, and the pneumatic control port is connected with an exhaust port through a pipeline. And hydraulic oil overflowing from the pressure control valve is discharged from the oil outlet. The pressure of the closed hydraulic part can be limited by controlling the opening and closing of the pressure control valve, and the actual overflow pressure can be automatically adjusted according to different exhaust pressures, so that the energy consumption of the system is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to an overflow control device for a booster compressor. Background Art

[0002] An ion compressor is a special type of positive displacement compressor. It primarily consists of a gas compression section, a hydraulic drive section, and a variable-diameter piston for transmission. Its operating principle is that in the hydraulic drive section, a reciprocating pump with a volume-changing chamber drives hydraulic oil into and out of the lower portion of a combined cylinder, which in turn drives the variable-diameter piston within the combined cylinder to reciprocate. Above the variable-diameter piston is the gas compression section, where intake and exhaust valves work together to complete the intake, compression, exhaust, and expansion processes. Ion compressors offer advantages such as excellent sealing performance, high volumetric efficiency, and large exhaust volume.

[0003] Overflow loss in the ion compressor process is the primary cause of energy loss. The magnitude of this loss is related to the overflow pressure. When the overflow pressure is excessive, the drive pump is required to perform work at high pressure. However, this work is not used to reciprocate the variable piston, but is instead converted into the internal energy of the overflowed hydraulic oil, resulting in energy waste. Furthermore, the gas pressure ranges of each compression stage vary, while the hydraulic pressure ranges are similar. Meeting the control requirements of each compression stage and reducing the production cost of the pressure control valve are also challenges that need to be addressed. Utility Model Content

[0004] In order to solve the problems of the prior art, the utility model provides a booster compressor overflow control device, which can limit the pressure of the closed hydraulic part by controlling the opening and closing of the pressure control valve, and can automatically adjust the actual overflow pressure according to the exhaust pressure, thereby reducing the energy consumption of the system.

[0005] The utility model provides an overflow control device for a booster compressor, comprising a combined cylinder body, a variable-diameter piston being arranged in the combined cylinder body, a gas chamber being formed above the variable-diameter piston, the gas chamber being connected to an air inlet and an exhaust port, a hydraulic oil chamber being formed below the variable-diameter piston, the hydraulic oil chamber being connected to a reciprocating pump via a connecting pipe, the reciprocating pump chamber, the hydraulic part of the combined cylinder body and the connecting pipe together forming a closed hydraulic part, the closed hydraulic part being connected to a pressure control valve, the pressure control valve comprising an oil supply port, an oil outlet port and an air control port, the oil supply port being connected to the closed hydraulic part via a pipe, the air control port being connected to the exhaust port via a pipe, and the hydraulic oil overflowing in the pressure control valve being discharged from the oil outlet port.

[0006] Further improvement, the pressure control valve also includes an external control port, a main valve and a pilot valve, the pilot valve includes a valve head and a valve core connected by a spring, one side of the valve head is subjected to the pressure of the oil supply port, and the valve core is subjected to the pressure of the air control port and the spring force; the external control port is connected to the oil supply port, and the main valve is arranged in the oil supply port. After the main valve is opened, the hydraulic oil in the oil supply port flows to the oil outlet, and the opening and closing of the main valve is controlled by the pilot valve and the external control port.

[0007] The booster compressor overflow control method of the booster compressor overflow control device is as follows: when the pressure of the closed hydraulic part is too high, the pressure control valve opens, and the hydraulic oil of the closed hydraulic part flows from the oil supply port to the oil outlet, thereby limiting the pressure of the closed hydraulic part; at the same time, an air control port is installed on the pressure control valve, and the pressure control valve automatically adjusts the overflow pressure according to the change of the exhaust pressure through the air control port.

[0008] The specific process of the pressure control valve adjusting the overflow pressure through the air control port is as follows:

[0009] When the pressure of the oil supply port is greater than the sum of the gas force of the air control port and the spring force of the pilot valve, the pilot valve opens, causing the pressure in front of the pilot valve to decrease, thereby causing the main valve to open and begin to overflow, and the hydraulic oil flows from the oil supply port to the oil outlet;

[0010] When the pressure at the oil supply port drops below the sum of the gas force at the air control port and the spring force of the pilot valve, the pilot valve closes, causing the main valve to close and the overflow to end.

[0011] The beneficial effects of the utility model are:

[0012] 1. Taking into account the influence of exhaust pressure changes on the overflow pressure of the oil supply port, the pressure of the closed hydraulic part can be limited by controlling the opening and closing of the pressure control valve.

[0013] 2. The pressure control valve only needs to replace a small number of parts to meet the control requirements of different compression levels, reducing the production cost of the pressure control valve.

[0014] 3. It can automatically adjust the actual overflow pressure according to the different exhaust pressures, thereby reducing the energy consumption of the system. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following briefly introduces the drawings required for use in the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0016] Figure 1 It is a principle diagram of the overflow control method of the booster compressor in the embodiment of the present utility model.

[0017] Figure 2 It is a structural diagram of the pressure control valve of the booster compressor in the embodiment of the present utility model.

[0018] Reference numerals:

[0019] 1. Oil supply port, 2. Oil outlet port, 3. External control port, 4. Main valve, 5. Pilot valve, 6. Air control port, 7. Air inlet port, 8. Exhaust port, 9. Combined cylinder, 10. Variable diameter piston, 11. Reciprocating pump, 12. Pressure control valve, 13. Closed hydraulic part, 14. Valve core. DETAILED DESCRIPTION

[0020] The following will be combined with the accompanying drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0021] like Figure 1 As shown, due to the working characteristics of the compressor, the gas on the upper side of the variable-diameter piston 10 needs to go through four stages in a single cycle, namely compression, exhaust, expansion, and intake. The gas pressure is in a fluctuating state in a single cycle, so the pressure of the closed hydraulic part 13 fluctuates within a certain range. The booster compressor overflow control method disclosed in the present utility model is that when the pressure of the closed hydraulic part 13 is too high, the pressure control valve 12 is opened, and the hydraulic oil of the closed hydraulic part 13 can flow from the oil supply port 1 to the oil outlet 2, thereby limiting the pressure of the closed hydraulic part 13. At the same time, the pressure control valve 12 can also automatically adjust the overflow pressure by taking into account the changes in the exhaust pressure through the air control port 6, thereby reducing the overflow energy consumption of the equipment.

[0022] The utility model discloses a preferred structure of a pressure control valve. Figure 2 As shown, in order to achieve automatic adjustment to a low-energy relief pressure that adapts to changing working conditions, the utility model adds an air control port 6 to the traditional plug-in relief valve. The gas pressure in the air control port 6 can act on the pilot valve spool 14. The pressure control valve 12 also includes an external control port 3, a main valve 4 and a pilot valve 5. The pilot valve 5 includes a valve head and a valve spool 14 connected by a spring. One side of the valve head is affected by the pressure of the oil supply port 1, and the valve spool 14 is affected by the pressure of the air control port 6 and the spring force. The external control port 3 is connected to the oil supply port 1, and the main valve 4 is arranged in the oil supply port 1. When the main valve 4 is opened, the hydraulic oil in the oil supply port 1 flows to the oil outlet 2. The opening and closing of the main valve 4 is controlled by the pilot valve 5 and the external control port 3.

[0023] When the pressure in oil supply port 1 does not meet the overflow condition, pilot valve 5 is closed. When the pressure in oil supply port 1 meets the overflow condition, the spool of pilot valve 5 overcomes the spring force and opens. Hydraulic oil flows through the valve gap of pilot valve 5, creating a pressure differential above and below main valve 4. This pressure differential causes main valve 4 to open, thereby achieving overflow through main valve 4.

[0024] When the pressure control valve 12 is operating normally with a relief valve, the external control port 3 is at a high pressure, and the opening and closing of the main valve 4 is primarily controlled by the opening and closing of the pilot valve 5. When the pressure control valve 12 needs to maintain a continuous relief valve state, the external control port 3 is placed in a low pressure state. At this time, a pressure differential is formed above and below the main valve 4, causing it to open.

[0025] When the pressure at the oil supply port 1 is greater than the sum of the gas force at the air control port 6 and the spring force of the pilot valve 5, the pilot valve 5 opens, causing the pressure in front of the pilot valve 5 to decrease, thereby causing the main valve 4 to open and overflow to begin, and the hydraulic oil to flow from the oil supply port 1 to the oil outlet 2. Similarly, when the pressure at the oil supply port 1 decreases and becomes less than the sum of the gas force at the air control port 6 and the spring force of the pilot valve 5, the pilot valve 5 closes, causing the main valve 4 to close and the overflow to end. The structural main body of the pressure control valve 12 of each compression stage is the same, and the only different parts are the size of the air control port 6 and the structural size of the side of the pilot valve spool 14 that is affected by the gas pressure. Therefore, different air control ports 6 and pilot valve spool 14 accessories can be replaced for pressure control valves 12 of different compression stages, which is convenient to replace and reduces the production cost of the pressure control valve.

[0026] Each embodiment in this specification is described in a progressive manner, and the same or similar parts between the embodiments can be referred to each other, and each embodiment focuses on the differences from other embodiments. In particular, for the device embodiment, the above is only a preferred implementation method of the present invention. Since it is basically similar to the method embodiment, the description is relatively simple, and the relevant parts can be referred to the partial description of the method embodiment. The above is only a specific implementation method of the present invention, but the protection scope of the present invention is not limited to this. Any technician familiar with this technical field is within the technical scope disclosed by this utility model. For ordinary technicians in this technical field, changes or replacements that can be easily thought of should be included in the protection scope of this utility model without departing from the principle of this utility model. Therefore, the protection scope of the present utility model should be based on the protection scope of the claims.

Claims

1. A booster compressor overflow control device, characterized in that: The invention comprises a combined cylinder body (9), wherein a variable-diameter piston (10) is provided in the combined cylinder body (9), a gas chamber is provided above the variable-diameter piston (10), the gas chamber is connected to an air inlet (7) and an air outlet (8), and a hydraulic oil chamber is provided below the variable-diameter piston (10). The hydraulic oil chamber is connected to a reciprocating pump (11) through a connecting pipe. The pump chamber of the reciprocating pump (1), the hydraulic part of the combined cylinder body (9), and the connecting pipe together constitute a closed hydraulic part (13), characterized in that: the closed hydraulic part (13) is connected to a pressure control valve (12), the pressure control valve (12) comprises an oil supply port (1), an oil outlet port (2), and an air control port (6), the oil supply port (1) is connected to the closed hydraulic part (13) through a pipe, the air control port (6) is connected to the air outlet (8) through a pipe, and the hydraulic oil overflowing from the pressure control valve (12) is discharged from the oil outlet port (2).

2. The booster compressor overflow control device according to claim 1, characterized in that: The pressure control valve (12) further comprises an external control port (3), a main valve (4) and a pilot valve (5); the pilot valve (5) comprises a valve head and a valve core (14) connected by a spring; one side of the valve head is subjected to the pressure of the oil supply port (1); the valve core (14) is subjected to the pressure of the air control port (6) and the spring force; the external control port (3) is communicated with the oil supply port (1); the main valve (4) is arranged in the oil supply port (1); after the main valve (4) is opened, the hydraulic oil in the oil supply port (1) flows to the oil outlet (2); the opening and closing of the main valve (4) is controlled by the pilot valve (5) and the external control port (3).

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