Energy-saving hydraulic self-adjusting air compressor

Abstract

The invention relates to the field of parts of energy-saving household appliances, in particular to an energy-saving hydraulic self-adjusting air compressor which comprises a piston cylinder and a piston arranged in the piston cylinder in a sliding mode, and first compression cavities used for being matched with the piston to compress air are formed in cavities, corresponding to the piston cylinder, of the two ends of the piston. A second compression cavity with the volume of L1 is formed in the piston cylinder, the second compression cavity is provided with an output end used for outputting gas to the outside and an input end used for inputting air, L1 is larger than 2Q # imgabs0 # delta t, Q is the flow of the single stroke of the piston, and delta t is the cycle time of the single stroke of the piston; an output port of the first compression cavity is provided with a control valve which is communicated with the second compression cavity and used for controlling gas output, at least one inner wall of the second compression cavity is provided with an elastic piece capable of elastically expanding and shrinking, and the second compression cavity is provided with a gas supplementing assembly which compresses the elastic piece in the overpressure process and expands the elastic piece in the underpressure process. According to the application, the fluctuation of the pressure and the flow of the output airflow can be obviously slowed down in a manner of supplementing air in time and temporarily storing overpressure air.

Description

Technical Field

[0001] The present application relates to the field of energy-saving household appliance parts and components, and in particular to an energy-saving hydraulic self-regulating air compressor. Background Art

[0002] Hydraulic air compressor is a gas compression device driven by hydraulic system, which compresses air by converting hydraulic energy into mechanical energy. Although its overall cost and dependence on hydraulic system are relatively high, its operation stability and energy utilization rate of more than 80% make it have the advantages of good explosion-proof performance, energy saving and high integration. Therefore, it is mostly used in air conditioning equipment in some independent residential areas, such as villas and other occasions.

[0003] Since hydraulic air compressors need to convert hydraulic energy into mechanical energy, the common method used is to use a piston to squeeze the gas in the piston cylinder, thereby converting the hydraulic energy into the mechanical energy of compressed air.

[0004] In actual use, since the piston compresses the air through reciprocating motion, there will be a certain blank period when the piston is reset, resulting in a pulsed gas flow. On the one hand, the pulsed airflow will cause vibrations in the gas delivery system; on the other hand, the pulsed airflow will reduce the heat exchange efficiency of the refrigerant and increase the power consumption of the compressor. Therefore, how to effectively reduce the airflow pulse of the hydraulic air compressor is a problem that needs to be solved at present. Summary of the invention

[0005] In order to effectively reduce the air flow pulse of the hydraulic air compressor, the present application provides an energy-saving hydraulic self-regulating air compressor.

[0006] The present application provides an energy-saving hydraulic self-regulating air compressor, which adopts the following technical solution: An energy-saving hydraulic self-regulating air compressor comprises a piston cylinder and a piston slidably arranged in the piston cylinder, wherein the chambers at both ends of the piston corresponding to the piston cylinder are formed with a first compression chamber for cooperating with the piston to compress air, and a second compression chamber with a volume of L1 is formed in the piston cylinder, and the second compression chamber is provided with an output end for outputting gas to the outside and an input end for inputting air, and L1>2Q δt, Q is the flow rate of a single stroke of the piston, and δt is the cycle time of a single stroke of the piston; the output port of the first compression chamber is provided with a control valve connected to the second compression chamber and used to control the gas output, at least one inner wall of the second compression chamber is provided with an elastic member that can expand and contract elastically, and the cavity wall or the outside of the second compression chamber is provided with an air replenishing component that compresses the elastic member when overpressure and expands the elastic member when underpressure.

[0007] Through the aforementioned technical scheme, when the piston reciprocates, one end of the piston can maintain compressed air and the other end absorbs external uncompressed air to shorten the blank period of outputting compressed air; at the same time, since the elastic member can expand and contract elastically and can be compressed or expanded by the air replenishing component, when the pressure is too high, the pressure of the air output from the second compression chamber and the upward fluctuation of the flow rate can be significantly reduced by compressing the elastic member and the air itself in a larger space; at the same time, when the pressure is under-pressure, the volume of the second compression chamber can also be reduced by the expansion of the elastic member, so that the second compression chamber can, on the one hand, reduce the compression pressure of the air, and on the other hand, can maintain a certain amount of compressed gas output when the piston compresses the air by reducing the space, and with the significantly reduced blank period, the pressure fluctuation and flow fluctuation during the compressed gas output can be significantly reduced, effectively reducing the airflow pulse of the hydraulic air compressor, and at the same time, the adjustment of the volume of the second compression chamber can be achieved in a limited space without the need for additional external space.

[0008] Optionally, the output port of the first compression chamber is opened on the inner wall of the end faces of both ends of the corresponding piston, and the control valve includes a control rod slidably connected to the inner wall of the second compression chamber along the output direction of the output port and a control spring for driving the control rod to slide toward the corresponding output port, and a control cover for pressing and sealing the outer cavity wall of the output port is fixed to one end of the control rod corresponding to the output port.

[0009] Through the aforementioned technical solution, the control spring drives the control cover to maintain a state of blocking the output port, and maintains a state of pressing the output port before the air is compressed to a corresponding pressure, so as to cooperate with the piston to compress the air, and after the pressure reaches the standard, the compressed air pushes the control cover away from the output port and compresses the control spring, so that the compressed gas can be output to the second compression chamber.

[0010] Optionally, a control hole is opened in the second compression chamber corresponding to the control rod, and a control seat threadedly connected to the control hole is provided at one end of the control rod away from the control cover and slides along the axial direction of the control rod, and two ends of the control spring are respectively pressed against the control seat and the control cover.

[0011] Through the above-mentioned technical solution, the control seat can be rotated to adjust the degree to which the control spring is compressed when the control cover is pressed against the output port, so as to adjust the pressure threshold of the output compressed air.

[0012] Optionally, the piston includes a piston shaft and compression seats fixed at both ends of the piston shaft, the piston shaft is penetrated and slidably provided with a connecting seat, the connecting seat is fixed to the inner wall of the piston cylinder and divides the cavity between the two compression seats into two independent driving chambers, and the driving chamber is provided with an oil passage for inputting or outputting external hydraulic oil.

[0013] Through the above-mentioned technical solution, the two driving chambers are respectively injected and output with hydraulic oil, which can cooperate with the axial sliding of the compression seat weir piston shaft to improve the compression energy conversion rate of the hydraulic oil.

[0014] Optionally, a limiting portion fixed to an inner wall of the driving cavity is respectively provided on one side of the two oil passages that are away from each other, and the limiting portion is used to limit the compression seat from sliding toward the connecting seat.

[0015] Through the above-mentioned technical solution, the sliding stroke of the compression seat can be limited to reduce the possibility of the compression seat blocking the oil passage.

[0016] Optionally, the elastic member is made of elastic material and is fitted to the inner wall of the second compression chamber. A plurality of buffer chambers interconnected with each other are formed inside the elastic member. The second compression chamber is connected to an air replenishing chamber for temporarily storing or releasing compressed gas in the buffer chamber. The air replenishing assembly includes an air replenishing piston slidably arranged in the air replenishing chamber and an air replenishing spring for driving the air replenishing piston to move toward a channel connecting the air replenishing chamber to the second compression chamber.

[0017] Through the aforementioned technical solution, the buffer chamber can further increase the amplitude of elastic expansion and contraction of the elastic member, thereby further increasing the space for regulating the compressed air pressure and output.

[0018] Optionally, an adjustment seat is penetrated through and threadedly connected to the inner wall of the air-filling chamber, and two ends of the air-filling spring are respectively abutted against the adjustment seat and the air-filling piston.

[0019] Through the aforementioned technical scheme, the degree of compression of the air supplement spring can be adjusted through the adjustment seat, so that the pressure required for the compression elastic member can adaptively change following the output pressure of the first compression chamber; at the same time, it is also possible to increase or decrease the air pressure in the buffer chamber by adjusting the air input or output of the buffer chamber, thereby adjusting the degree of compression of the elastic member under the same pressure to further adapt the piston stroke.

[0020] Optionally, the gas-replenishing piston includes a gas-replenishing cover adapted to the gas-replenishing chamber and a gas-replenishing rod fixed to the gas-replenishing cover, the gas-replenishing rod is plugged and slidably connected to the adjustment seat, and the gas-replenishing spring is sheathed on the gas-replenishing rod and abuts against the adjustment seat.

[0021] Through the above-mentioned technical solution, when the elastic member is compressed, the squeezed air is input into the air replenishment chamber, and pushes and compresses the air replenishment cover, further buffering the pressure, and assisting the elastic member to expand and release the compressed air.

[0022] Optionally, the control rod is a tubular structure and is covered with and slidably connected to an adjustment rod arranged at a corresponding output end, the output end is a hole, and the adjustment rod is smaller than the aperture of the output port of the first compression chamber, and the end of the control rod away from the control cover is connected to an adjustment channel, and the adjustment channel is connected to a cavity on the side of the channel of the air replenishment piston in the air replenishment chamber away from the air replenishment chamber connecting the buffer chamber.

[0023] Through the aforementioned technical solution, when the air pressure output from the first compression chamber is too high, the air supply spring will be over-compressed. At this time, the air compressed by the corresponding air supply cover can drive the adjusting rod to slide toward the output port to reduce the channel size of the output port, and then enter the second compression chamber. The space suddenly becomes larger, further achieving the purpose of buffering and real-time regulation of the output pressure.

[0024] Optionally, the elastic member is laid on at least 4 / 5 of the inner wall of the second compression chamber.

[0025] Through the above-mentioned technical solution, the margin for regulating the space of the second compression chamber can be significantly increased by laying out the elastic members over a large area, thereby further optimizing the margin for regulating the compressed air.

[0026] In summary, the present application includes at least one of the following beneficial technical effects: During the process of the first compression chamber outputting air, the fluctuation of air pressure and flow rate will cause the output to be a pulsed airflow. δt will make the airflow output from the first compression chamber flow into the second compression chamber with a significantly larger volume. If the compressed gas cannot output the pressure in time and is too high, on the one hand, the gas will be compressed for the second time in the second compression chamber with a larger space, reducing the pressure and flow rate fluctuations of the gas output from the second compression chamber; at the same time, the elastic member will be compressed, so that the volume of the second compression chamber can be significantly increased in a short time, further reducing the pressure fluctuations and flow rate fluctuations; and during the blank period when the compressed gas is output from the first compression chamber, the volume of the second compression chamber can be reduced by the reset expansion of the elastic member, and the compressed gas of the corresponding pressure can be supplemented to the outside in time, so as to maintain the continuity and stability of the compressed air output, reduce the damage to the pipeline and the influence on the heat exchange efficiency, and achieve the purpose of energy saving. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 It is a schematic diagram of the cross-sectional structure of an embodiment of the present application.

[0028] Figure 2 yes Figure 1 Schematic diagram of the enlarged structure of part A.

[0029] Explanation of the accompanying drawings: 1. Piston cylinder; 10. Elastic member; 101. Buffer chamber; 11. First compression chamber; 111. One-way valve; 112. Electromagnet; 12. Second compression chamber; 121. Control hole; 122. Air supply chamber; 123. Pressure valve; 13. Connecting seat; 14. Drive chamber; 141. Limiting part; 15. Oil passage; 2. Piston; 21. Piston shaft; 22. Compression seat; 3. Control valve; 31. Control rod; 311. Control cover; 312. Adjusting rod; 32. Control spring; 33. Control seat; 331. Connecting hole; 4. Air supply assembly; 41. Air supply piston; 411. Air supply cover; 412. Air supply rod; 42. Air supply spring; 43. Adjusting seat; 44. Adjusting passage. DETAILED DESCRIPTION

[0030] The following is combined with Figure 1 and Figure 2 This application is described in further detail.

[0031] The present application discloses an energy-saving hydraulic self-regulating air compressor. Figure 1 and Figure 2 The air compressor includes a piston cylinder 1 and a piston 2. A first compression chamber 11 is formed in the piston cylinder 1. The piston 2 is slidably disposed in the first compression chamber 11 and is used for compressing air.

[0032] Specifically, the first compression chamber 11 is a cylindrical structure, and the piston 2 includes a piston shaft 21 and a compression seat 22 fixed to both ends of the piston shaft 21. The piston shaft 21 is coaxially arranged in the first compression chamber 11, and a connecting seat 13 is fixed in the middle of the axial direction of the first compression chamber 11 to divide the first compression chamber 11 into two chambers. The piston shaft 21 is penetrated and slidably connected to the connecting seat 13 to serve as a guide and foundation for the sliding of the piston shaft 21. The cross section of the compression seat 22 is adapted to the first compression chamber 11 for compressing air.

[0033] The connecting seat 13 divides the cavity between the two compression seats 22 into two independent driving chambers 14. The driving chamber 14 is provided with an oil passage 15 for inputting or outputting external hydraulic oil, so that hydraulic oil can be input through one of the oil passages 15. At the same time, the other oil passage 15 opens or extracts the hydraulic oil in the corresponding driving chamber 14, which can push the compression seat 22 to slide axially in the first compression chamber 11; and because there are two compression seats 22 sliding, at least one of the cavities on the side away from the two compression seats 22 maintains a compressed air state and reciprocates, which can make the piston 2 always maintain a relatively stable compressed air output from the end of the first compression chamber 11 corresponding to the two compression seats 22 away from each other during the sliding process, except for the compression gap where the air pressure does not meet the standard.

[0034] The two oil passages 15 are provided with limiting parts 141 fixed to the inner wall of the driving chamber 14 on the side away from each other. The limiting parts 141 are used to limit the compression seat 22 from sliding toward the connecting seat 13 to avoid the compression seat 22 blocking the oil passage 15.

[0035] Reference Figure 1 and Figure 2 At the same time, since the compression seat 22 needs to move a certain stroke so that the air can be compressed to the corresponding pressure before it can be output, a second compression chamber 12 is formed in the piston cylinder 1. The second compression chamber 12 is located at the side of the first compression chamber 11 and has a volume of L1, L1>2Q δt, Q is the flow rate of a single stroke of the piston, and δt is the cycle time of a single stroke of the piston so that when the pressure in the second compression chamber 12 increases and the flow rate increases rapidly, the overall compressed air in a larger space can be further compressed to a smaller amount, thereby achieving the same degree of mitigation of pressure fluctuations.

[0036] The inner wall of the first compression chamber 11 located on the side away from the two compression seats 22 is respectively provided with an output port for outputting the compressed gas to the second compression chamber 12 for temporary storage, and outputting the compressed gas through the second compression chamber 12. A pressure valve 123 for outputting the compressed gas is provided in the middle of the side of the second compression chamber 12 away from the first compression chamber 11. Among them, the inner wall of the first compression chamber 11 located on the side away from the two compression seats 22 is respectively provided with an input port for introducing external air, and the input port is provided with a one-way input check valve 111 for controlling the input of gas; the check valve 111 can be set as a solenoid valve or a one-way open valve.

[0037] In order to control the output gas pressure and close the output port of the first compression chamber 11, a control valve 3 for controlling the gas output is provided at the output port of the first compression chamber 11, and the output port of the first compression chamber 11 is opened on the inner wall corresponding to the end faces of the piston 2 at both ends.

[0038] The control valve 3 includes a control rod 31 slidably connected to the inner wall of the second compression chamber 12 along the output direction of the output port and a control spring 32 for driving the control rod 31 to slide toward the corresponding output port, and a control cover 311 for pressing and blocking the cavity wall of the second compression chamber 12 on one side of the output port is fixed at one end of the control rod 31 corresponding to the output port. The outer wall of the second compression chamber 12 on the side of the output port corresponding to the output port is formed with an annular groove adapted to the control cover 311 to optimize the blocking effect of the output port.

[0039] Reference Figure 1 and Figure 2, a control hole 121 is provided at the position corresponding to the output port of the second compression chamber 12, that is, the control hole 121 is provided corresponding to the control rod 31, and the control hole 121 is parallel to the piston shaft 21. A control seat 33 is sleeved on one end of the control rod 31 away from the control cover 311, and the control seat 33 is axially slidably matched with the control rod 31, and the control seat 33 is threadedly connected to the control hole 121 and sealed. The two ends of the control spring 32 are respectively pressed against the control seat 33 and the control cover 311, and the control spring 32 is sleeved on the control rod 31 and is in a compressed state, so that the air in the first compression chamber 11 can be compressed to meet a certain pressure, and the control cover 311 can be used to compress the control spring 32 and open the output port of the first compression chamber 11, and the compressed air can be output to the second compression chamber 12 for temporary storage. Among them, the control cover 311 is made of magnetic metal or has magnetic metal embedded inside, and the output port of the first compression chamber 11 is provided with an electromagnet 112 for adsorbing the control cover 311, and the electromagnet 112 can be controlled by an electronic control system to reduce the possibility of air leakage during the compression process due to slight deformation of the control spring 32 when the pressure of the compressed air is insufficient.

[0040] At the same time, the distance between the control seat 33 and the control cover 311 can be controlled by rotating the control seat 33, and the degree of compression of the control spring 32 can be adjusted, so as to cooperate with the electromagnet 112 to adjust the pressure of the output compressed air; at the same time, when the compression seat 22 moves toward the connecting seat 13, the corresponding control cover 311 can be timely abutted and cooperated with the output port of the first compression chamber 11 to reduce the possibility of drawing the air in the second compression chamber 12 back to the first compression chamber 11.

[0041] Reference Figure 1 and Figure 2 In addition, in order to timely replenish the compressed gas of corresponding pressure into the second compression chamber 12 during the process of compressing air and maintain the continuity and stability of the compressed air output, the inner wall or the outside of the second compression chamber 12 is provided with an air replenishment component 4 for absorbing gas under overpressure and releasing gas under underpressure, so as to maintain the stability and continuity of the output air pressure and reduce the damage to the pipeline and the influence on the heat exchange efficiency. In the embodiment of the present application, the air replenishment component 4 is arranged outside the second compression chamber 12, that is, arranged on the outer wall of the piston cylinder 1.

[0042] Specifically, at least part of the inner wall of the second compression chamber 12 is fixed with an elastic member 10, and at least 4 / 5 of the interior of the second compression chamber 12 is paved with the elastic member 10, preferably, except for the inner wall of the area corresponding to the output port and other gas input or output areas, the elastic member 10 is fixed with the elastic member 10. The elastic member 10 is made of elastic material, so that the volume of the second compression chamber 12 can be changed within a certain range through the expansion and contraction of the elastic member 10. That is, the elastic member 10 is compressed at high pressure and high flow, so that the space for accommodating compressed gas in the second compression chamber 12 becomes larger, and the purpose of further reducing the upward fluctuation of air pressure is achieved by accommodating more gas and compressing the same volume of air in a larger space.

[0043] At the same time, during the blank period when the first compression chamber 11 outputs compressed gas, the elastic member 10 can expand to reduce the space of the second compression chamber 12, so that during the blank period when the compressed gas is output, the compressed gas can be output toward the outside by squeezing the space, thereby reducing the lower limit of the output compressed gas pressure and flow rate, thereby releasing the space in the high-pressure chamber to reduce the upward fluctuation of the compressed gas, and expanding during underpressure to make the space of the second compression chamber 12 smaller, filling the blank period when the compressed gas is output, thereby significantly reducing the fluctuation of the output airflow pressure and the fluctuation of the flow rate, and reducing the airflow pulse of the output air.

[0044] The side of the second compression chamber 12 is formed with a gas replenishing chamber 122, which can be an external container or a cavity formed on the inner wall of the piston cylinder 1. In this embodiment, the gas replenishing chamber 122 is an external container, preferably a tubular external container. The elastic member 11 is internally formed with a plurality of interconnected buffer chambers 101, and one of the buffer chambers 101 is connected to the gas replenishing chamber 122 to further increase the amplitude of the spatial change of the second compression chamber 12, and the buffer chambers 101 can be interconnected through a hole structure or through a pipeline.

[0045] The air replenishment chamber 122 is used to temporarily store part of the gas squeezed out when the buffer chamber 101 is over-pressurized or to release the temporarily stored gas toward the buffer chamber 101 when under-pressurized. The inner wall of the air replenishment chamber 122 is a cylindrical structure.

[0046] Reference Figure 1 and Figure 2The air replenishment assembly 4 includes an air replenishment piston 41 slidably connected to the air replenishment chamber 122 and an air replenishment spring 42 for driving the air replenishment piston 41 to move toward the passage connecting the air replenishment chamber 122 to the buffer chamber 101. The air replenishment piston 41 includes an air replenishment cap 411 adapted to the cross section of the air replenishment chamber 122 and an air replenishment rod 412 fixed to the air replenishment cap 411, the air replenishment rod 412 is plugged and slidably connected to the adjustment seat 43, and the air replenishment spring 42 is sheathed on the air replenishment rod 412. An adjustment seat 43 is coaxially arranged on the inner wall of the air-making chamber 122 and threadedly connected thereto. Two ends of the air-making spring 42 are respectively abutted against the adjustment seat 43 and the air-making cover 411, so that the gas pressed out of the buffer cavity 101 can be temporarily stored in the air-making chamber 122. When one of the compression seats 22 is reset and the other compression seat 22 compresses the air, the gas in the air-making chamber 122 is squeezed into the buffer cavity 101 in time through the air-making spring 42 to replenish the compressed air required in the reset process. The degree of compression of the air-making spring 42 can be adjusted through the adjustment seat 43, and the expansion and contraction amplitude of the elastic member 10 can be adjusted to adapt to the pressure of the compressed air in the first compression cavity 11.

[0047] In addition, in order to avoid the situation where the pressure of the output compressed gas is too high due to excessive pressure, the control rod 31 is a tubular structure and is covered and slidably connected with an adjustment rod 312 provided at the corresponding output end, and the output end is a hole structure. Among them, the inner wall of the control rod 31 is a stepped shaft structure and the large end is the end away from the first compression chamber 11. The adjustment rod 312 is adapted to the inner wall of the control rod 31 and the small end extends toward the output port of the first compression chamber 11, so as to reduce the output cross section of the output port when overpressure occurs, reduce the output flow rate, and reduce the situation where the output compressed air pressure is too high.

[0048] The adjusting rod 312 is smaller than the aperture of the output port of the first compression chamber 11. The end of the control rod 31 away from the control cover 311 is connected to the adjusting channel 44. The adjusting channel 44 is connected to the cavity on the side of the channel connecting the air replenishing piston 41 in the air replenishing chamber 122 away from the air replenishing chamber 122 and the buffer chamber 101.

[0049] Reference Figure 1 and Figure 2, the regulating channel 44 can be set as a hole channel in the piston cylinder 1, or as a pipeline. In this embodiment, the control seat 33 is provided with a connecting hole 331 coaxially arranged with the regulating rod 312, the regulating channel 44 is a pipeline, and one end of the regulating channel 44 is fixed and connected to the connecting hole 331, and the other end of the regulating channel 44 is fixed to the regulating seat 43 and connected to the air replenishing chamber 122 through the regulating seat 43. When the air in the second compression chamber 12 is over-pressured, the elastic member 10 will be compressed, so that the buffer chamber 101 is compressed and the air replenishing spring 42 is compressed. At this time, the air replenishing cover 411 will compress the air between the regulating seat 43 and the air replenishing cover 411. At this time, the compressed air will drive the regulating rod 312 to move toward the output port of the first compression chamber 11 and reduce the cross-sectional area of ​​the air flow flowing through the output port of the first compression chamber 11, so as to reduce the output flow rate and reduce the possibility of a sharp increase in pressure.

[0050] Finally, in order to reduce the resistance to the movement of the adjusting rod 312 , the end of the adjusting rod 312 facing the first compression chamber 11 is tapered.

[0051] The above are all preferred embodiments of the present application, and the protection scope of the present application is not limited thereto. Therefore, any equivalent changes made according to the structure, shape, and principle of the present application should be included in the protection scope of the present application.

Claims

1. An energy-saving hydraulic self-regulating air compressor, comprising a piston cylinder (1) and a piston (2) slidably arranged in the piston cylinder (1), characterized in that: The chambers at both ends of the piston (2) corresponding to the piston cylinder (1) are each formed with a first compression chamber (11) for cooperating with the piston (2) to compress air, and a second compression chamber (12) with a volume of L1 is formed in the piston cylinder (1), and the second compression chamber (12) is provided with an output end for outputting gas to the outside and an input end for inputting air, and L1>2Q δt, Q is the flow rate of a single stroke of the piston (2), and δt is the cycle time of a single stroke of the piston (2); the output port of the first compression chamber (11) is provided with a control valve (3) which is connected to the second compression chamber (12) and is used to control the gas output; at least one inner wall of the second compression chamber (12) is provided with an elastic member (10) which can elastically expand and contract; the chamber wall or the outside of the second compression chamber (12) is provided with an air replenishing component (4) which compresses the elastic member (10) when overpressure occurs and expands the elastic member (10) when underpressure occurs.

2. An energy-saving hydraulic self-regulating air compressor according to claim 1, characterized in that: The output port of the first compression chamber (11) is formed on the inner wall of the end faces of both ends of the corresponding piston (2); the control valve (3) comprises a control rod (31) slidably connected to the inner wall of the second compression chamber (12) along the output direction of the output port, and a control spring (32) for driving the control rod (31) to slide toward the corresponding output port; a control cover (311) for pressing and blocking the outer cavity wall of the output port is fixed to one end of the control rod (31) corresponding to the output port.

3. An energy-saving hydraulic self-regulating air compressor according to claim 2, characterized in that: The second compression chamber (12) is provided with a control hole (121) corresponding to the control rod (31); one end of the control rod (31) away from the control cover (311) is sleeved with a control seat (33) threadedly connected to the control hole (121) and slidably arranged along the axial direction of the control rod (31); and two ends of the control spring (32) are respectively pressed against the control seat (33) and the control cover (311).

4. The energy-saving hydraulic self-regulating air compressor according to claim 1, characterized in that: The piston (2) comprises a piston shaft (21) and compression seats (22) fixed at both ends of the piston shaft (21); a connecting seat (13) is slidably provided through the piston shaft (21); the connecting seat (13) is fixed to the inner wall of the piston cylinder (1) and divides the cavity between the two compression seats (22) into two independent driving chambers (14); the driving chamber (14) is provided with an oil passage (15) for inputting or outputting external hydraulic oil.

5. The energy-saving hydraulic self-regulating air compressor according to claim 4, characterized in that: A limiting portion (141) fixed to the inner wall of the driving chamber (14) is provided on one side of the two oil passages (15) that are away from each other. The limiting portion (141) is used to limit the compression seat (22) from sliding toward the connecting seat (13).

6. The energy-saving hydraulic self-regulating air compressor according to claim 2, characterized in that: The elastic member (10) is made of elastic material and is fitted to the inner wall of the second compression chamber (12). A plurality of mutually connected buffer chambers (101) are formed inside the elastic member (10). The second compression chamber (12) is connected to an air replenishing chamber (122) for temporarily storing or releasing compressed gas in the buffer chamber (101). The air replenishing assembly (4) comprises an air replenishing piston (41) slidably arranged in the air replenishing chamber (122) and an air replenishing spring (42) for driving the air replenishing piston (41) to move toward a passage connecting the air replenishing chamber (122) to the second compression chamber (12).

7. An energy-saving hydraulic self-regulating air compressor according to claim 6, characterized in that: An adjustment seat (43) is penetrated through the inner wall of the air replenishment chamber (122) and is threadedly connected thereto. Two ends of the air replenishment spring (42) are respectively in contact with the adjustment seat (43) and the air replenishment piston (41).

8. The energy-saving hydraulic self-regulating air compressor according to claim 7, characterized in that: The gas replenishing piston (41) comprises a gas replenishing cover (411) adapted to the gas replenishing chamber (122) and a gas replenishing rod (412) fixed to the gas replenishing cover (411); the gas replenishing rod (412) is plugged into and slidably connected to the adjustment seat (43); the gas replenishing spring (42) is sheathed on the gas replenishing rod (412) and abuts against the adjustment seat (43).

9. The energy-saving hydraulic self-regulating air compressor according to claim 6, characterized in that: The control rod (31) is a tubular structure and is covered with and slidably connected to an adjustment rod (312) provided at a corresponding output end, the output end being a hole, and the adjustment rod (312) is smaller than the hole diameter of the output port of the first compression chamber (11), and one end of the control rod (31) away from the control cover (311) is connected to an adjustment channel (44), and the adjustment channel (44) is connected to a cavity on one side of a channel of the air replenishment piston (41) in the air replenishment chamber (122) away from the air replenishment chamber (122) and connected to the buffer chamber (101).

10. The energy-saving hydraulic self-regulating air compressor according to claim 6, characterized in that: The elastic member (10) is laid on at least 4 / 5 of the inner wall of the second compression chamber (12).

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