CN217327585U

CN217327585U - Hydraulic gas compressor

Info

Publication number: CN217327585U
Application number: CN202122804410.XU
Authority: CN
Inventors: 朱学斌
Original assignee: Individual
Current assignee: Individual
Priority date: 2021-11-16
Filing date: 2021-11-16
Publication date: 2022-08-30
Anticipated expiration: 2031-11-16

Abstract

The utility model discloses a hydraulic gas compressor, which comprises a tank A, a tank B and a bidirectional liquid pressure pump; the lower parts of the tank A and the tank B are filled with liquid; the lower part of the tank A is provided with a tank A liquid inlet and outlet pipe, the upper part of the tank A is provided with a tank A gas outlet valve, and the tank A is provided with a tank A gas inlet valve; the lower part of the tank B is provided with a tank B liquid inlet and outlet pipe, the upper part of the tank B is provided with a tank B gas outlet valve, and the tank B is provided with a tank B gas inlet valve; two ends of the liquid pressure pump are respectively connected with the liquid inlet and outlet pipe of the tank A and the liquid inlet and outlet pipe of the tank B. The utility model discloses utilize high-pressure liquid to come compressed air, compare traditional air compressor, the energy use is efficient, and the noise is little, can produce the pure compressed gas who does not have oil pollution, and the energy efficiency is high and the optimal model regulation of present national standard reaches the standard value and can reach 20%, and no oil pollution gas's special application occasion can reach 30%, can make huge contribution for the energy saving and emission reduction in the world.

Description

Hydraulic gas compressor

Technical Field

The utility model relates to a gas compression equipment field, concretely relates to pneumatic compressor.

Background

The gas compressor is widely applied to the fields of gas storage and transportation and production and manufacturing. The compressor is commonly provided with four types of compressors, namely a reciprocating piston compressor, an oil-injection screw compressor, an oil-injection scroll compressor and an oil-injection sliding vane compressor, most of the compressors are components such as a motor-driven piston or a screw rod for directly compressing gas, and the common characteristics of low energy use efficiency and large noise exist.

The hydraulic air compressor (patent number: CN200720149117.1) is not commonly used, the energy use efficiency is high, the noise is low, but the hydraulic air compressor can be used only by a matching liquid storage pool, so that the manufacturing cost is high, the occupied area is large, the installation is inconvenient, the movement is inconvenient, the installation and movement costs are high, the liquid discharge and air suction process is realized, the liquid in the air cylinder has potential energy to flow back to the liquid storage pool to suck the gas into the air cylinder, the energy waste is caused, the output pressure requirement of the matching liquid pressure pump is increased, and the cost of the liquid pressure pump is increased.

The centrifugal liquid pressure pump has the advantages of high energy use efficiency, stable performance, durability, simple structure, low manufacturing cost, easy manufacture, long-term maintenance-free and low noise, is widely applied to various industries, and is the most suitable pump type for the liquid pressure pump selected by the hydraulic air compressor. However, the centrifugal liquid booster pump used in the hydraulic air compressor has some serious disadvantages, and corresponding measures are required to be taken against the disadvantages. Specifically, the method comprises the following steps: centrifugal liquid force (forcing) pump is high-efficient stable only near its design flow, design lift operating mode, and the skew design flow of operating mode, design lift operating mode can descend by a wide margin, and output resistance is low can lead to output flow super large, supporting motor probably overload operation, the cavitation phenomenon damages accessory in the pump, cavitation phenomenon noise is big in the pump. The hydraulic air compressor compresses gas, the gas is easy to compress at the initial stage of each gas compression period and has low resistance, the output resistance of the centrifugal liquid pressurizing pump is low, the problems of overlarge output flow, possible overload operation of a matched motor, damage to accessories in the pump due to cavitation in the pump and high noise due to cavitation are caused, and the energy use efficiency is very low; in the middle period of each gas compression period, the compression resistance is increased, the output resistance of the centrifugal liquid pressurizing pump is increased, the initial problems can be reduced or eliminated, and the energy use efficiency is low; every gas compression cycle later stage, the compression resistance increase is close design flow, design lift operating mode gradually, and the initial stage problem just can be eliminated gradually completely, and the energy uses the efficient to promote the best gradually.

SUMMERY OF THE UTILITY MODEL

For the not enough to prior art exists, the utility model provides a follow-on gas compressor that surges.

In order to achieve the above object, the utility model adopts the following technical scheme:

a kind of liquid pneumatic compressor, including A pot, B pot and two-way liquid booster pump; the lower parts of the tank A and the tank B are filled with liquid; the lower part of the tank A is provided with a tank A liquid inlet and outlet pipe, the upper part of the tank A is provided with a tank A gas outlet valve, and the tank A is provided with a tank A gas inlet valve; the lower part of the tank B is provided with a tank B liquid inlet and outlet pipe, the upper part of the tank B is provided with a tank B gas outlet valve, and the tank B is provided with a tank B gas inlet valve; two ends of the liquid pressure pump are respectively connected with the liquid inlet and outlet pipe of the tank A and the liquid inlet and outlet pipe of the tank B.

Further, the bidirectional liquid pressure pump is provided with a tank A pressure position and a tank B pressure position, when the reversing valve is located at the tank B pressure position, the tank A air inlet valve is opened, the tank B air inlet valve and the tank B air outlet valve are closed, liquid at the lower part of the tank A is injected into the lower part of the tank B through the bidirectional liquid pressure pump in a pressure mode, and air at the upper part of the tank B is compressed; when the reversing valve is positioned at the pressurizing position of the tank A, the air inlet valve of the tank B is opened, the air inlet valve of the tank A and the air outlet valve of the tank A are closed, and liquid at the lower part of the tank B is pressurized and injected into the lower part of the tank A through the bidirectional liquid pressurizing pump to compress air at the upper part of the tank A.

Further, when the tank B is required to supply air to the outside, the air outlet valve of the tank B is opened, so that the tank B is communicated with the compressed gas outlet.

Further, when the tank A is required to supply air to the outside, the air outlet valve of the tank A is opened, so that the tank A is communicated with the compressed gas outlet.

Furthermore, a tank A flow control valve is arranged on the tank A liquid inlet and outlet pipe, and a tank A flow bypass pipe is connected in parallel at two ends of the tank A flow control valve.

Furthermore, a tank B flow control valve is arranged on the liquid inlet and outlet pipe of the tank B, and a tank B flow bypass pipe is connected in parallel at two ends of the tank B flow control valve.

Further, the bidirectional liquid pressure pump is matched with a rotating speed adjusting device.

Furthermore, the air outlet valve of the tank A and the air outlet valve of the tank B adopt any one of a check valve, an electric control valve, a pneumatic valve or a mechanical control valve.

Furthermore, the air inlet valve of the tank A and the air inlet valve of the tank B adopt any one of a check valve, an electric control valve, a pneumatic valve or a mechanical control valve.

Further, the tank A pressurization process and the tank B pressurization process are alternately executed in a staggered way, so that the continuous compression of the gas is realized.

Furthermore, the gas compression process of the tank A and the gas compression process of the tank B are alternately executed in time staggered, so that continuous compression of gas is realized.

Compared with the prior art, the beneficial effects of the utility model are that:

1. need not to form a complete set extra cistern, the cost descends by a wide margin, reduces area, promotes installation and removal convenience, has reduced installation and removal cost.

2. The potential energy waste of liquid in the cylinder flowing back to the liquid storage pool is avoided, the energy is effectively saved, the output pressure of the matched liquid pressure pump is reduced, and the cost is effectively reduced.

3. The characteristic adaptation technology is adopted for matching the liquid booster pump with the hydraulic air compressor, the defects of a centrifugal liquid booster pump matched with the hydraulic air compressor are overcome, and a foundation is laid for large-scale use of the hydraulic air compressor, and the characteristics of high energy use efficiency, low noise and capability of purifying oil-free polluted gas.

4. The energy efficiency is higher than the standard value of the optimal machine type regulation of the existing national standard and can reach 20%, the special application occasion without oil pollution gas can reach 30%, and the energy-saving and emission-reducing device can make great contribution to the world.

Drawings

Fig. 1 is a schematic structural view of a hydraulic gas compressor of the present invention;

description of reference numerals: 1-A tank inlet and outlet pipe; 2-a bidirectional liquid pressure pump; 3-A tank liquid; 4-A tank; 5-A tank gas; 6-A tank air inlet valve; 7-A tank air outlet valve; 8-A tank air inlet; a 9-A tank compressed gas outlet; a compressed gas outlet of the 10-B tank; 11-tank B gas inlet; a 12-B tank gas outlet valve; 13-tank B inlet valve; 14-B tank gas; 15-B tank; tank 16-B liquid; and a liquid inlet and outlet pipe of the 17-B tank.

Detailed Description

In order to make the objects, technical solutions and effects of the present invention clearer and clearer, the present invention will be described in further detail with reference to the accompanying drawings and the following detailed description.

Examples

As shown in fig. 1, the liquid gas compressor mainly comprises an a tank 4, a B tank 15 and a bidirectional liquid booster pump 2. The lower parts of the A tank 4 and the B tank 5 are filled with liquid, and the upper parts of the liquid are filled with air. The lower part of the A tank 4 is provided with a tank A liquid inlet and outlet pipe 1, the upper part of the A tank 4 is provided with a tank A gas outlet valve 7, and the A tank 4 is provided with a tank A gas inlet valve 6. The lower part of the B tank 15 is provided with a B tank liquid inlet and outlet pipe 17, the upper part of the B tank 15 is provided with a B tank gas outlet valve 12, and the B tank 15 is provided with a B tank gas inlet valve 13. Two ends of the bidirectional liquid pressure pump 2 are respectively connected with the tank A liquid inlet and outlet pipe 1 and the tank B liquid inlet and outlet pipe 17.

The working principle is as follows:

the process of injecting the liquid 3 in the tank A into the tank B15 under pressure (referred to as forward pressurization process for short): the air outlet valve 7 of the tank A is closed, the air inlet valve 13 of the tank B is closed, the bidirectional liquid pressure pump 2 is started to perform positive pressure operation, the air inlet valve 6 of the tank A is opened, gas to be compressed enters the tank A4 from the air inlet 8 of the tank A, the liquid 3 of the tank A flows through the liquid inlet and outlet pipe 1 of the tank A and enters the bidirectional liquid pressure pump 2, the gas flows through the liquid inlet and outlet pipe 17 of the tank B after being pressurized and is injected into the tank B15, the liquid level of the liquid 16 of the tank B rises to compress the gas 14 of the tank B, when the pressure of the tank B15 rises to a set value, the air outlet valve 12 of the tank B is opened, the gas 14 of the tank B flows through the air outlet valve 12 of the tank B, the compressed gas outlet 10 of the tank B supplies air, the gas 5 of the tank A gradually increases, the liquid 3 of the tank A gradually decreases, the liquid 16 of the tank B gradually increases, the gas 14 of the tank B gradually decreases, the bidirectional liquid pressure pump 2 stops operating after a period of time, and the air outlet valve 12 of the tank B closes.

The process of injecting the liquid 16 in the tank B into the tank A4 under pressure (referred to as reverse pressurization process for short): the air outlet valve 12 of the tank B is closed, the air inlet valve 6 of the tank A is closed, the bidirectional liquid pressure pump 2 is started to perform reverse pressure operation, the air inlet valve 13 of the tank B is opened, gas to be compressed enters the tank B15 from the air inlet 11 of the tank B, liquid 16 of the tank B flows through the liquid inlet and outlet pipe 17 of the tank B and enters the bidirectional liquid pressure pump 2, the gas flows through the liquid inlet and outlet pipe 1 of the tank A after being pressurized and is injected into the tank A4, the liquid level of the liquid 3 of the tank A rises to compress the gas 5 of the tank A, when the pressure of the tank A4 rises to a set value, the air outlet valve 7 of the tank A is opened, the gas 5 of the tank A flows through the air outlet valve 7 of the tank A, the compressed gas outlet 9 of the tank A supplies air, the gas 14 of the tank B gradually increases, the liquid 16 of the tank B gradually decreases, the liquid 3 of the tank A gradually increases, the gas 5 of the tank A gradually decreases, the bidirectional liquid pressure pump 2 stops operating after a period of time, and the air outlet valve 7 of the tank A is closed.

The forward pressurizing process and the reverse pressurizing process are alternately executed in a staggered mode, continuous compression of gas is achieved, and the compressed gas outlet 9 of the tank A and the compressed gas outlet 10 of the tank B can be communicated and combined into one compressed gas outlet.

It is easy to understand that the bidirectional liquid pressure pump 2 can also adopt a common unidirectional liquid pressure pump to be matched with a corresponding reversing valve to realize the forward and reverse reversing function of an inlet and an outlet, for example, can adopt a four-way valve and a corresponding pipeline to realize the reversing function.

The A tank air outlet valve 7 and the B tank air outlet valve 12 can be selected from various valves such as a check valve, an electric control valve, a pneumatic valve, a mechanical control valve and the like, and are not limited by the types of the valves. If jar A air outlet valve 7 chooses the check valve for use, in the check valve import intercommunication jar A4, export intercommunication jar A compressed gas outlet 9, jar A gas 5 can flow to jar A compressed gas outlet 9, and jar A compressed gas outlet 9 communicates the gas of outside air supply pipe can not flow to jar A4 in. If the B tank gas outlet valve 12 is a check valve, the inlet of the check valve is communicated with the B tank 15, the outlet of the check valve is communicated with the B tank compressed gas outlet 10, the B tank gas 14 can flow to the B tank compressed gas outlet 10, and the gas of an external gas supply pipe communicated with the B tank compressed gas outlet 10 can not flow to the B tank 15.

The air inlet valve 6 of the tank A and the air inlet valve 13 of the tank B can be selected from various valves such as a check valve, an electric control valve, a pneumatic valve, a mechanical control valve and the like, and are not limited by the types of the valves. If jar A admission valve 6 chooses the check valve for use, in the check valve export intercommunication jar 4, the gas that needs the compression can flow in jar 4A, jar A gas 5 and jar A liquid 3 in jar 4A can not flow to jar A air inlet 8, jar B admission valve 13 chooses the check valve for use, in the check valve export intercommunication jar B15, the gas that needs the compression can flow in jar 15B, jar B gas 14 and jar B liquid 16 in jar B15 can not flow to jar B air inlet 11.

The bidirectional liquid pressure pump 2 adopts a centrifugal liquid pressure pump, has high energy use efficiency, stable performance, durability, simple structure, low manufacturing cost, easy manufacture, long-term maintenance-free and low noise, is widely applied to various industries, and is the most suitable pump type for the liquid pressure pump selected by the hydraulic air compressor.

However, the centrifugal liquid pressure pump is efficient and stable only near the design flow and the design lift working condition, the working condition deviates from the design flow and the design lift working condition, the energy use effective rate can be greatly reduced, the output resistance is low, the output flow is overlarge, the matching motor can run in an overload mode, the cavitation phenomenon in the pump damages accessories, and the cavitation phenomenon noise is large.

In order to solve the problem, a control valve can be serially arranged on a liquid outlet pipe of the bidirectional liquid pressure pump 2 and connected with a bypass pipe, specifically: the tank A flow control valve is arranged on the tank A liquid inlet and outlet pipe 1, and the two ends of the tank A flow control valve are connected with a tank A flow bypass pipe in parallel; the tank B liquid inlet and outlet pipe 17 is provided with a tank B flow control valve, and two ends of the tank B flow control valve are connected with a tank B flow bypass pipe in parallel.

The bypass pipe is connected in parallel, the drift diameter of the control valve can be reduced, the cost is reduced, the drift diameter of the bypass pipe can be configured according to the flow limited to pass through at the initial stage of each gas compression period, the control valve at the initial stage of each gas compression period is closed, the outflow of the centrifugal liquid pressurizing pump flows through the bypass pipe, the flow is limited within a certain range, the flow is not overlarge, the problems that the motor is possibly overloaded to run due to low output resistance, the accessories in the pump are damaged by the cavitation phenomenon in the pump, and the cavitation phenomenon noise is large can be solved.

Meanwhile, the mode that the control valve is connected with the bypass pipe in parallel can be replaced by a mode of changing the running rotating speed of the centrifugal liquid pressure pump, and specifically comprises the following steps: the method comprises the steps of carrying out performance test on a centrifugal liquid booster pump selected and matched with a hydraulic gas compressor, measuring the high-efficiency no-overload rotating speed of the liquid booster pump at a plurality of output resistance points in each gas compression period, recording rotating speed data into a control system, measuring the flow corresponding to the rotating speed according to the volume of a matched tank and each output resistance point, calculating the duration time between the resistance points, recording the duration time between the resistance points into the control system, and controlling the liquid booster pump to operate by the control system according to the time and rotating speed characteristics of each gas compression period, so that the liquid booster pump at each output resistance point in each gas compression period can keep high-efficiency operation.

If the liquid pressure pump is driven by a motor, the speed can be regulated by methods such as a frequency converter and the like; if the liquid pressure pump is driven by an oil-burning machine, the speed can be regulated by methods such as controlling an accelerator and the like, and if the liquid pressure pump is driven by a water turbine, the speed can be regulated by methods such as controlling the water quantity and the like, and the speed regulation method is not limited.

In the embodiment, a common machine type is selected for comparison, the rated exhaust pressure is 0.7MPa, the rated power of a driving motor is 7.5KW, and the optimal energy efficiency grade of each type of compressor specified in national standard GB19153-2019 'energy efficiency limit value and energy efficiency grade of positive displacement air compressor' is specifically as follows:

remarking: smaller specific power units in the table indicate more energy savings.

In conclusion, the hydraulic gas compressor of the application utilizes high-pressure liquid to compress air, compared with the traditional air compressor, the hydraulic gas compressor has the advantages of high energy use efficiency, low noise, capability of generating pure compressed gas without oil pollution, high energy efficiency which can reach 20% of the specified value of the optimal model of the national standard, capability of reaching 30% of the special application occasion of the gas without oil pollution, and great contribution to energy conservation and emission reduction in the world.

The above detailed description is specific to possible embodiments of the present invention, and the embodiments are not intended to limit the scope of the present invention, and all equivalent implementations or modifications that do not depart from the scope of the present invention should be included within the scope of the present invention.

Claims

1. A kind of liquid pneumatic compressor, characterized by: comprises a tank A, a tank B and a bidirectional liquid pressure pump; the lower parts of the tank A and the tank B are filled with liquid; the lower part of the tank A is provided with a tank A liquid inlet and outlet pipe, the upper part of the tank A is provided with a tank A gas outlet valve, and the tank A is provided with a tank A gas inlet valve; the lower part of the tank B is provided with a tank B liquid inlet and outlet pipe, the upper part of the tank B is provided with a tank B gas outlet valve, and the tank B is provided with a tank B gas inlet valve; two ends of the liquid pressure pump are respectively connected with the liquid inlet and outlet pipe of the tank A and the liquid inlet and outlet pipe of the tank B.

2. The hydro-pneumatic compressor as claimed in claim 1, wherein: the bidirectional liquid pressure pump is provided with a tank A pressure position and a tank B pressure position, when the reversing valve is positioned at the tank B pressure position, the tank A air inlet valve is opened, the tank B air inlet valve and the tank B air outlet valve are closed, liquid at the lower part of the tank A is injected into the lower part of the tank B through the bidirectional liquid pressure pump in a pressure mode, and air at the upper part of the tank B is compressed; when the reversing valve is positioned at the pressurizing position of the tank A, the air inlet valve of the tank B is opened, the air inlet valve of the tank A and the air outlet valve of the tank A are closed, and the liquid at the lower part of the tank B is pressurized and injected into the lower part of the tank A through the bidirectional liquid pressurizing pump to compress the air at the upper part of the tank A.

3. The hydro-pneumatic compressor as claimed in claim 1, wherein: a tank flow control valve is arranged on the liquid inlet pipe and the liquid outlet pipe of the tank A, and a tank A flow bypass pipe is connected in parallel at two ends of the tank A flow control valve.

4. The hydro-pneumatic compressor as claimed in claim 3, wherein: and a tank B flow control valve is arranged on the liquid inlet and outlet pipe of the tank B, and two ends of the tank B flow control valve are connected with a tank B flow bypass pipe in parallel.

5. The hydro-pneumatic compressor as claimed in claim 1, wherein: the bidirectional liquid pressure pump is matched with a rotating speed adjusting device.

6. The hydro-pneumatic compressor as defined by claim 1 wherein: the tank A air outlet valve and the tank B air outlet valve adopt any one of a check valve, an electric control valve, a pneumatic valve or a mechanical control valve.

7. The hydro-pneumatic compressor as claimed in claim 1, wherein: the air inlet valve of the tank A and the air inlet valve of the tank B adopt any one of a check valve, an electric control valve, a pneumatic valve or a mechanical control valve.