阅读说明：本技术 双作用气动液压泵 (Double-acting pneumatic hydraulic pump ) 是由 晁鲁强 陈永正 庄圳生 山云霄 邴文法 岳崇平 于 2021-07-06 设计创作，主要内容包括：双作用气动液压泵,包括有配合连接的上盖体和下盖体,在上盖体和下盖体之间设有泵体承托板,泵体承托板将上盖体和下盖体内的空腔分为上腔体和下腔体,在泵体承托板上安装有气动液压泵总成,所述气动液压泵总成包括有第一缸盖和第二缸盖,第一缸盖和第二缸盖之间由气缸筒相连接,在气缸筒内还安装有能在第一缸盖和第二缸盖之间移动的活塞,活塞将气缸筒内分成两个独立的活塞腔,所述活塞上安装有柱塞,柱塞一端穿出第一缸盖并配合安装有第一泵油体,柱塞另一端穿出第二缸盖并配合安装有第二泵油体,所述柱塞能跟随活塞在第一泵油体和第二泵油体内往复移动。(A double-acting pneumatic hydraulic pump comprises an upper cover body and a lower cover body which are connected in a matching way, a pump body bearing plate is arranged between the upper cover body and the lower cover body, the pump body bearing plate divides a cavity in the upper cover body and the lower cover body into an upper cavity and a lower cavity, a pneumatic hydraulic pump assembly is arranged on the pump body bearing plate, the pneumatic hydraulic pump assembly comprises a first cylinder cover and a second cylinder cover, the first cylinder cover and the second cylinder cover are connected by a cylinder barrel, a piston which can move between the first cylinder cover and the second cylinder cover is also arranged in the cylinder barrel and divides the cylinder barrel into two independent piston cavities, install the plunger on the piston, first cylinder cap is worn out and the cooperation is installed first pump oil body to plunger one end, and the second cylinder cap is worn out and the cooperation is installed the second pump oil body to the plunger other end, the plunger can be followed the piston at first pump oil body and the internal reciprocating motion of second pump oil.)

1. A double-acting pneumatic hydraulic pump characterized by: the pneumatic hydraulic pump comprises an upper cover body (1) and a lower cover body (2) which are connected in a matching manner, a pump body bearing plate (3) is arranged between the upper cover body (1) and the lower cover body (2), a cavity in the upper cover body (1) and the lower cover body (2) is divided into an upper cavity (4) and a lower cavity (5) by the pump body bearing plate (3), a pneumatic hydraulic pump assembly is arranged on the pump body bearing plate (3) and comprises a first cylinder cover (6) and a second cylinder cover (7), the first cylinder cover (6) and the second cylinder cover (7) are connected through a cylinder barrel (8), a piston (9) capable of moving between the first cylinder cover (6) and the second cylinder cover (7) is further arranged in the cylinder barrel (8), the piston (9) divides the cylinder barrel (8) into two independent piston cavities, a plunger (10) is arranged on the piston (9), one end of the plunger (10) penetrates through the first cylinder cover (6) and is provided with a first pump oil body (11) in a matching manner, the other end of the plunger (10) penetrates through the second cylinder cover (7) and is provided with a second oil pumping body (12) in a matched mode, the plunger (10) can move back and forth in the first oil pumping body (11) and the second oil pumping body (12) along with the piston (9), the first oil pumping body (11) is connected with a first oil suction valve (13), the second oil pumping body (12) is connected with a second oil suction valve (14), the first oil suction valve (13) and the second oil suction valve (14) penetrate through the pump body bearing plate (3) and extend into the lower cavity (5), one-way valves are arranged in the first oil suction valve (13) and the second oil suction valve (14) and allow a hydraulic medium in the oil suction valves to flow into the oil pumping body; a second one-way valve (74) is mounted at an oil outlet of the second oil pumping body (12), and a first one-way valve (73) is mounted at an oil outlet of the first oil pumping body (11); the first cylinder cover (6) and the second cylinder cover (7) are respectively provided with an air inlet and an air outlet, the pneumatic hydraulic pump assembly is also provided with a pneumatic control assembly capable of driving the piston (9) to reciprocate, and the pneumatic control assembly is communicated with the two air inlet and outlet holes;

an air inlet blasting device is arranged on an air inlet pipeline (76) of the pneumatic control assembly; the air inlet burst blowing device comprises a dustproof valve assembly, a high-pressure air inlet pipe (18), a silencer (19) and an oil-water separator (20), wherein the dustproof valve assembly comprises a dustproof valve body (21) and a dustproof valve core shaft (22) which are matched with each other, the high-pressure air inlet pipe (18), the silencer (19) and the oil-water separator (20) are respectively communicated with an inner cavity of the dustproof valve body (21), the oil-water separator (20) is communicated with a pneumatic control assembly through a pipeline, a dustproof valve air inlet channel (23) communicated with the oil-water separator (20) is further arranged in the dustproof valve body (21), an arc-shaped groove (24) is formed in the dustproof valve core shaft (22) positioned in the dustproof valve body (21), a limit stop (25) and a handle (26) are installed at the upper end, extending out of the dustproof valve body (21), and a retaining column (27) matched with the limit stop (25) is installed on the dustproof valve body (21), when the handle (26) is rotated to one end of the limit stop (25) and is contacted with the stop column (27), the arc-shaped groove (24) can communicate the silencer (19) with the oil-water separator (20), when the handle (26) is rotated to the other end of the limit stop (25) and is contacted with the stop column (27), the arc-shaped groove (24) can communicate the high-pressure air inlet pipe (18) with the dust valve air inlet channel (23), and the arc-shaped groove (24) can communicate the high-pressure air inlet pipe (18) with the silencer (19) in the rotating process.

2. A double acting pneumatic hydraulic pump as claimed in claim 1, wherein: the pneumatic control assembly comprises a gas circuit reversing valve (28) installed on a first cylinder cover (6), a pneumatic valve core (29) is installed in the gas circuit reversing valve (28) in a matched mode, one end of the gas circuit reversing valve (28) is communicated with a main air inlet connector (30), a pneumatic valve core spring seat (31) is installed at the other end of the gas circuit reversing valve (28), a pneumatic valve core spring (72) is installed on the pneumatic valve core spring seat (31), a first cavity (32), a second cavity (33), a third cavity (34), a fourth cavity (35), a fifth cavity (36) and a spring cavity (37) are arranged in a valve body of the gas circuit reversing valve (28), a first boss (38), a second boss (39), a third boss (40) and a fourth boss (41) are arranged on the periphery of the pneumatic valve core (29), first sealing rings (42) are arranged on the first boss (38), the second boss (39), the third boss (40) and the fourth boss (41), wherein the diameters of the first boss (38), the second boss (39) and the third boss (40) are the same and are smaller than the diameter of the fourth boss (41), the third cavity (34) and the fifth cavity (36) are matched with the first boss (38), the second boss (39) and the third boss (40), the spring cavity (37) is matched with the fourth boss (41), the inner part of the pneumatic valve core (29) is an air inlet cavity (43) and a spring cavity (44), the air inlet cavity (43) and the spring cavity (44) are respectively positioned at two sides of the third boss (40), a pneumatic valve core spring (72) is matched with the spring cavity (44), a valve core (45) communicated with the air inlet cavity (43) is further arranged on the pneumatic valve core (29) between the second boss (39) and the third boss (40), a first air channel (46) communicated with the first cavity (32) is further arranged inside the valve body of the pneumatic circuit directional control valve (28), a first pump body air passage (47) communicated with the second cavity (33), an exhaust port (48) communicated with the third cavity (34), a second pump body air passage (49) communicated with the fourth cavity (35), a third air passage (51) communicated with the spring cavity (37), a second air passage (50) communicated with the first air passage (46), a third pump body air passage (52) communicated with the first pump body air passage (47) and arranged in the first cylinder cover (6), a pump body air hole (53) arranged on the inner side of the second cylinder cover (7), a third pump body air passage (52) communicated with the pump body air hole (53) through a first vent pipe (54), a fourth pump body air passage (55) communicated with the second pump body air passage (49) and arranged in the first cylinder cover (6), a fourth pump body air passage (55) communicated with the cylinder barrel (8), and a fourth air passage (56) communicated with the second air passage (50) and arranged in the first cylinder cover (6), a fifth air passage (57) communicated with the third air passage (51), a first reversing control valve (58) is installed in the first cylinder cover (6), a fourth air passage (56) and the fifth air passage (57) are communicated with the first reversing control valve (58), a second reversing control valve (59) is installed on the second cylinder cover (7), an exhaust air passage (60) communicated with the second reversing control valve (59) is arranged in the second cylinder cover (7), a sixth air passage (61) communicated with the first reversing control valve (58) is arranged in the first cylinder cover (6), a seventh air passage (62) communicated with the second reversing control valve (59) is arranged in the second cylinder cover (7), a second communicating pipe (63) is installed between the sixth air passage (61) and the seventh air passage (62), and when the first reversing control valve (58) is touched by the piston (9), the fourth air passage (56) is communicated with the fifth air passage (57), the fourth boss (41) is positioned in a spring cavity (37) far away from one end of the pneumatic valve core spring seat (31), the second boss (39) and the third boss (40) are positioned on two sides of the fourth cavity (35), the first boss (38) is positioned between the first cavity (32) and the second cavity (33), the valve core air hole (45) is communicated with the fourth cavity (35), the first pump body air passage (47) is communicated with the exhaust port (48), the first cavity (32) is not communicated with the second cavity (33), when the piston (9) triggers the second reversing control valve (59), the exhaust air passage (60) is communicated with the seventh air passage (62), the sixth air passage (61) is communicated with the fifth air passage (57), the fourth boss (41) is positioned in the spring cavity (37) close to one end of the pneumatic valve core spring seat (31), the second boss (39) and the third boss (40) are positioned in the fifth cavity (36), the first boss (38) is located in the third cavity (34), the first cavity (32) is communicated with the second cavity (33), and the second pump body air passage (49) is communicated with the exhaust port (48).

3. A double acting pneumatic hydraulic pump as claimed in claim 2, wherein: two pump body air holes (53) are formed in the inner side of the second cylinder cover (7), and the third pump body air passage (52) is divided into two paths and is respectively communicated with the pump body air holes (53) through a first air pipe (54).

4. A double acting pneumatic hydraulic pump as claimed in claim 2, wherein: the first reversing control valve (58) comprises a first reversing valve spring seat (64) arranged on the outer side of the first cylinder cover (6) and a first reversing control valve sleeve (65) arranged on the inner side of the first cylinder cover (6), a first control valve spool (66) is arranged in the first reversing control valve sleeve (65) in a matched mode, the end portion of the first control valve spool (66) penetrates through the first reversing control valve sleeve (65) and is located in the cylinder barrel (8), a first reversing valve spring (67) is arranged between the first control valve spool (66) and the first reversing valve spring seat (64), the first reversing valve spring (67) always tends to enable the fourth air passage (56) to be closed, and the fifth air passage (57) and the sixth air passage (61) are always communicated with the first reversing control valve sleeve (65).

5. A double acting pneumatic hydraulic pump as claimed in claim 2, wherein: the second reversing control valve (59) comprises a second reversing valve spring seat (68) arranged on the outer side of the second cylinder cover (7) and a second reversing control valve sleeve (69) arranged on the inner side of the second cylinder cover (7), a second control valve spool (70) is arranged in the second reversing control valve sleeve (69) in a matched mode, the end portion of the second control valve spool (70) penetrates through the second reversing control valve sleeve (69) and is located in the cylinder barrel (8), a second reversing valve spring (71) is arranged between the second control valve spool (70) and the second reversing valve spring seat (68), the second reversing valve spring (71) always tends to enable the seventh air channel (62) to be closed, and the exhaust air channel (60) is communicated with the second reversing control valve sleeve (69).

6. A double acting pneumatic hydraulic pump as claimed in claim 1, wherein: the hydraulic pump is characterized in that a four-way valve (75) is mounted on the second one-way valve (74), a first one-way valve (73) is mounted on and connected with an oil pipe (15), the first one-way valve only allows hydraulic medium in the first pump oil body (11) to flow to the connected oil pipe (15), the connected oil pipe (15) is communicated with the four-way valve (75), an oil outlet valve body (16) and an overflow valve assembly (17) are respectively connected to the other two oil holes of the four-way valve (75), and the piston (9) can repeatedly move to continuously convey the hydraulic medium in the lower cavity (5) to the oil outlet valve body (16).

Technical Field

The invention relates to the technical field of pneumatic hydraulic pumps, in particular to a double-acting pneumatic hydraulic pump.

Background

The pneumatic hydraulic pump is a novel conveying machine, adopts compressed air as a power source, converts lower air pressure into high-pressure oil, namely utilizes the low air pressure of a large-area piston end to generate high hydraulic pressure of a small-area piston end, and for various corrosive liquids, liquid with particles, high-viscosity, volatile, inflammable and extremely toxic liquid can be pumped out and sucked up by all kinds of liquid, so that the pneumatic hydraulic pump can be used in cooperation with an anchor cable tensioning machine, an anchor withdrawing machine, an anchor rod tension meter or other hydraulic tools instead of a manual or electric hydraulic pump. Most of the existing pneumatic hydraulic pumps are provided with a linkage oil pumping device on a piston, and the reciprocating movement of the piston completes one-time oil pumping, but the oil pumping mode generally cannot realize uninterrupted oil pumping, and the efficiency is lower.

Disclosure of Invention

The invention aims to provide a double-acting pneumatic hydraulic pump, which can pump oil by mounting oil pumping bodies at two ends of a piston of a hydraulic pump assembly, can pump oil by moving the piston once, can pump oil twice without interruption by reciprocating movement, improves the oil pumping efficiency and can solve the problems in the prior art.

The technical scheme adopted by the invention for solving the technical problems is as follows: a double-acting pneumatic hydraulic pump comprises an upper cover body and a lower cover body which are connected in a matching way, a pump body bearing plate is arranged between the upper cover body and the lower cover body, the pump body bearing plate divides a cavity in the upper cover body and the lower cover body into an upper cavity and a lower cavity, a pneumatic hydraulic pump assembly is arranged on the pump body bearing plate, the pneumatic hydraulic pump assembly comprises a first cylinder cover and a second cylinder cover, the first cylinder cover and the second cylinder cover are connected through a cylinder barrel, a piston capable of moving between the first cylinder cover and the second cylinder cover is also arranged in the cylinder barrel, the piston divides the cylinder barrel into two independent piston cavities, a plunger is arranged on the piston, one end of the plunger penetrates through the first cylinder cover and is matched with the first pump oil body, the other end of the plunger penetrates through the second cylinder cover and is matched with the second pump oil body, the plunger can move in a reciprocating way in the first pump oil body and the second pump oil body along with the piston, the first oil pumping body is connected with a first oil suction valve, the second oil pumping body is connected with a second oil suction valve, the first oil suction valve and the second oil suction valve penetrate through the pump body bearing plate and extend into the lower cavity, one-way valves are mounted in the first oil suction valve and the second oil suction valve, and the one-way valves allow a hydraulic medium in the oil suction valves to flow into the oil pumping bodies; a second one-way valve is mounted on an oil outlet of the second oil pumping body, and a first one-way valve is mounted on an oil outlet of the first oil pumping body; and the first cylinder cover and the second cylinder cover are respectively provided with an air inlet and outlet hole, the pneumatic hydraulic pump assembly is also provided with a pneumatic control assembly capable of driving the piston to reciprocate, and the pneumatic control assembly is communicated with the two air inlet and outlet holes.

An air inlet blasting device is arranged on an air inlet pipeline of the pneumatic control assembly; the air inlet burst-blowing device comprises a dustproof valve assembly, a high-pressure air inlet pipe, a silencer and an oil-water separator, wherein the dustproof valve assembly comprises a dustproof valve body and a dustproof valve mandrel which are matched with each other, the high-pressure air inlet pipe, the silencer and the oil-water separator are respectively communicated with an inner cavity of the dustproof valve body, the oil-water separator is communicated with the pneumatic control assembly through a pipeline, a dustproof valve air inlet channel communicated with the oil-water separator is also arranged in the dustproof valve body, an arc-shaped groove is formed in the dustproof valve mandrel in the dustproof valve body, a limit stop and a handle are arranged at the upper end, extending out of the dustproof valve body, of the dustproof valve mandrel, a retaining column matched with the limit stop is arranged on the dustproof valve body, when the handle is rotated to one end of the limit stop to be contacted with the retaining column, the arc-shaped groove can communicate the silencer with the oil-water separator, and when the handle is rotated to the other end of the limit stop to be contacted with the retaining column, the arc-shaped groove can communicate the high-pressure air inlet pipe with the air inlet channel of the dustproof valve, and the arc-shaped groove can communicate the high-pressure air inlet pipe with the silencer in the rotating process. The pneumatic control assembly comprises a gas path reversing valve arranged on a first cylinder cover, a pneumatic valve core is arranged in the gas path reversing valve in a matched manner, a main air inlet connector is communicated with one end of the gas path reversing valve, a pneumatic valve core spring seat is arranged at the other end of the gas path reversing valve, a pneumatic valve core spring is arranged on the pneumatic valve core spring seat, a first cavity, a second cavity, a third cavity, a fourth cavity, a fifth cavity and a spring cavity are arranged in a valve body of the gas path reversing valve, a first boss, a second boss, a third boss and a fourth boss are arranged on the periphery of the pneumatic valve core, first sealing rings are arranged on the first boss, the second boss, the third boss and the fourth boss, the diameters of the first boss, the second boss and the third boss are the same and are smaller than the diameter of the fourth boss, and the third cavity and the fifth cavity are matched with the first boss, the second boss and the third boss, the spring cavity is matched with the fourth boss, the inner part of the pneumatic valve core is an air inlet cavity and a spring cavity, the air inlet cavity and the spring cavity are respectively positioned at two sides of the third boss, a pneumatic valve core spring is matched with the spring cavity, a valve core air hole communicated with the air inlet cavity is also formed on the pneumatic valve core between the second boss and the third boss, a first air passage communicated with the first cavity, a first pump body air passage communicated with the second cavity, an air outlet communicated with the third cavity, a second pump body air passage communicated with the fourth cavity and a third air passage communicated with the spring cavity are also formed in the valve body of the air path reversing valve, the first air passage is communicated with the second air passage, a third pump body air passage communicated with the first pump body air passage is formed in the first cylinder cover, a pump body air hole is formed in the inner side of the second cylinder cover, and the third pump body air passage is communicated with the pump body air hole through a first air pipe, the first cylinder cover is internally provided with a fourth pump body air passage communicated with the second pump body air passage, the fourth pump body air passage is communicated with the cylinder barrel, the first cylinder cover is internally provided with a fourth air passage communicated with the second air passage and a fifth air passage communicated with the third air passage, the first cylinder cover is internally provided with a first reversing control valve, the fourth air passage and the fifth air passage are communicated with the first reversing control valve, the second cylinder cover is internally provided with a second reversing control valve, the second cylinder cover is internally provided with an exhaust air passage communicated with the second reversing control valve, the first cylinder cover is internally provided with a sixth air passage communicated with the first reversing control valve, the second cylinder cover is internally provided with a seventh air passage communicated with the second reversing control valve, a second communicating pipe is arranged between the sixth air passage and the seventh air passage, and when the piston touches the first reversing control valve, the fourth air passage is communicated with the fifth air passage, the fourth boss is located in a spring cavity far away from one end of a pneumatic valve core spring seat, the second boss and the third boss are located on two sides of the fourth cavity, the first boss is located between the first cavity and the second cavity, a valve core air hole is communicated with the fourth cavity, the first pump body air passage is communicated with an air outlet, the first cavity is not communicated with the second cavity, when the piston touches the second reversing control valve, the exhaust air passage is communicated with the seventh air passage, the sixth air passage is communicated with the fifth air passage, the fourth boss is located in the spring cavity close to one end of the pneumatic valve core spring seat, the second boss and the third boss are located in the fifth cavity, the first boss is located in the third cavity, the first cavity is communicated with the second cavity, and the second pump body air passage is communicated with the air outlet. Two pump body air holes are formed in the inner side of the second cylinder cover, and the third pump body air passage is divided into two paths and is respectively communicated with the pump body air holes through a first vent pipe. The first reversing control valve comprises a first reversing valve spring seat arranged on the outer side of the first cylinder cover and a first reversing control valve sleeve arranged on the inner side of the first cylinder cover, a first control valve core is arranged in the first reversing control valve sleeve in a matched mode, the end portion of the first control valve core penetrates through the first reversing control valve sleeve and is located in the cylinder barrel, a first reversing valve spring is arranged between the first control valve core and the first reversing valve spring seat, the first reversing valve spring always tends to seal a fourth air channel, and the fifth air channel and the sixth air channel are always communicated with the first reversing control valve sleeve. The second reversing control valve comprises a second reversing valve spring seat arranged on the outer side of the second cylinder cover and a second reversing control valve sleeve arranged on the inner side of the second cylinder cover, a second control valve spool is arranged in the second reversing control valve sleeve in a matched mode, the end portion of the second control valve spool penetrates through the second reversing control valve sleeve and is located in the cylinder barrel, a second reversing valve spring is arranged between the second control valve spool and the second reversing valve spring seat, the second reversing valve spring always tends to seal a seventh air channel, and the exhaust air channel is communicated with the second reversing control valve sleeve. The four-way valve is mounted on the second one-way valve, the first one-way valve is mounted and connected with the oil pipe, the first one-way valve only allows the hydraulic medium in the first pump oil body to flow to the connecting oil pipe, the connecting oil pipe is communicated with the four-way valve, the other two oil holes of the four-way valve are respectively connected with the oil outlet valve body and the overflow valve assembly, and the piston can move repeatedly to convey the hydraulic medium in the lower cavity to the oil outlet valve body uninterruptedly.

The invention has the positive effects that: according to the double-acting pneumatic hydraulic pump, the oil pumping bodies are arranged at the two ends of the piston of the hydraulic pump assembly, so that oil pumping can be realized when the piston moves once, oil pumping can be realized twice uninterruptedly by reciprocating movement, and the oil pumping efficiency is improved. And the air inlet blasting device for blasting and dedusting is arranged on the air inlet pipeline of the hydraulic pump assembly to ensure the cleanliness of an air supply source and ensure the normal work of the hydraulic pump assembly, and the pneumatic control assembly can realize the automatic reversing of the piston when the piston moves to the reversing control valve at the cylinder cover position, and realize uninterrupted oil pumping by continuously controlling the reciprocating movement of the piston.

Drawings

FIG. 1 is a schematic three-dimensional structure of the present invention; FIG. 2 is a front view of the present invention; FIG. 3 is a schematic three-dimensional structure of a pneumatic hydraulic pump assembly; FIG. 4 is a front view of the pneumatic hydraulic pump assembly; FIG. 5 is a schematic structural diagram of an air inlet blowout device; FIG. 6 is a schematic structural view of a dust valve assembly; FIG. 7 is an enlarged view of the cross-sectional view taken along line A-A of FIG. 6; FIG. 8 is a schematic view of the internal structure of the gas circuit directional control valve; FIG. 8a is an axial cross-sectional view of the valve body of the air passage directional control valve; FIG. 9 is a sectional view taken along line B-B of FIG. 8; FIG. 10 is a schematic view of the pneumatic valve spool of FIG. 8 moved closer to the pneumatic valve spool spring seat; FIG. 11 is a rear view of the gas circuit directional control valve; FIG. 12 is a schematic structural view of a pneumatic valve cartridge; FIG. 13 is a schematic structural view of an internal air passage of the first cylinder head; FIG. 14 is a cross-sectional view of the fourth airway and the fifth airway of FIG. 13; FIG. 15 is a cross-sectional view of the fifth airway and the sixth airway of FIG. 13; FIG. 16 is a schematic diagram of the second cylinder head internal air passage; FIG. 17 is a cross-sectional view of the seventh air passage and exhaust air passage of FIG. 16; FIG. 18 is a schematic illustration of the piston moving into contact with the first directional control valve; FIG. 19 is a schematic view of the piston moving into contact with the second directional control valve; FIG. 20 is a schematic structural view of a first directional control valve; fig. 21 is a schematic structural view of a second directional control valve.

Detailed Description

The invention relates to a double-acting pneumatic hydraulic pump, which comprises an upper cover body 1 and a lower cover body 2 which are connected in a matching way as shown in figure 1. As shown in fig. 2, a pump body support plate 3 is provided between the upper cover body l and the lower cover body 2. The pump body bearing plate 3 divides the cavity in the upper cover body 1 and the lower cover body 2 into an upper cavity 4 and a lower cavity 5, wherein the lower cavity 5 is filled with hydraulic oil medium.

And a pneumatic hydraulic pump assembly is arranged on the pump body bearing plate 3. The pneumatic hydraulic pump assembly is located in the upper chamber 4, and as shown in fig. 3, the pneumatic hydraulic pump assembly includes a first cylinder cover 6 and a second cylinder cover 7. The first cylinder cover 6 and the second cylinder cover 7 are connected by a cylinder barrel 8. As shown in fig. 4, a piston 9 is further mounted in the cylinder bore 8 so as to be movable between the first cylinder head 6 and the second cylinder head 7. A plunger 10 is mounted on the piston 9. One end of the plunger 10 penetrates through the first cylinder cover 6 and is provided with a first oil pumping body 11 in a matching mode, and the other end of the plunger 10 penetrates through the second cylinder cover 7 and is provided with a second oil pumping body 12 in a matching mode. The plunger 10 is capable of reciprocating in the first pumping body 11 and the second pumping body 12 following the piston 9. The piston 9 divides the interior of the cylinder bore 8 into two separate piston chambers, a first piston chamber 80 and a second piston chamber 81.

As shown in fig. 4, the first oil suction valve 13 is connected to the first oil pumping body 11, and the second oil suction valve 14 is connected to the second oil pumping body 12. The first oil suction valve 13 and the second oil suction valve 14 both penetrate through the pump body bearing plate 3 and extend into the lower cavity 5. One-way valves are respectively arranged in the first oil suction valve 13 and the second oil suction valve 14, only allow the hydraulic medium in the oil suction valves to flow into the oil pumping body, and prevent the hydraulic medium in the first oil suction valve 13 and the second oil suction valve 14 from flowing back into the lower cavity 5. The hydraulic medium may be an existing hydraulic oil. As shown in fig. 3, a connecting oil pipe 15 is installed between the first oil pumping body 11 and the second oil pumping body 12. The end of the connecting oil pipe 15 connected to the first oil pumping body 11 is provided with a first check valve 73, which only allows the hydraulic medium in the first oil pumping body 11 to flow to the connecting oil pipe 15. A second check valve 74 is mounted on the second oil pumping body 12. As shown in fig. 3, the second check valve and the connecting oil pipe 15 are connected together to form a four-way valve, and the other two oil holes of the four-way valve are respectively connected to an oil outlet valve body 16 and a relief valve assembly 17, wherein the oil outlet valve body 16 is located at the upper part of the upper cover body 1. The first cylinder cover 6 and the second cylinder cover 7 are respectively provided with an air inlet and an air outlet.

The repeated movement of the piston 9 in the cylinder 8 can synchronously drive the plunger 10 to reciprocate in the first pumping body 11 and the second pumping body 12. When the plunger 10 moves away from the first oil pumping body 11, hydraulic oil is sucked into the first oil pumping body 11 through the first oil suction valve 13, and at the moment, the synchronous plunger 10 extends into the second oil pumping body 12 to pressurize and convey the hydraulic oil in the second oil pumping body 12 to the oil outlet valve body 16; when the plunger 10 moves away from the second oil pumping body 12, hydraulic oil is sucked into the second oil pumping body 12 through the second oil suction valve 14, and at the moment, the synchronous plunger 10 extends into the first oil pumping body 11, so that the hydraulic oil in the first oil pumping body 11 is pressurized and conveyed to the oil outlet valve body 16 through the connecting oil pipe 15; no matter what state the piston 9 is in, uninterrupted oil pumping to the oil outlet valve body 16 can be guaranteed, namely the piston 9 reciprocates once, and the oil pumping bodies on the two sides pump primary hydraulic oil to the oil outlet valve body 16, so that double-acting oil pumping is realized. And because the existence of check valve, the condition that hydraulic oil refluxes does not exist in the oil pumping process.

In order to realize the reversing of the piston 9 in the reciprocating movement process, a pneumatic control assembly capable of driving the piston 9 to reciprocate is further installed on the pneumatic hydraulic pump assembly. The pneumatic control assembly is communicated with the two air inlet and outlet holes so that when air enters the air inlet and outlet holes of the first cylinder cover 6, the piston 9 moves towards the second cylinder cover 7, and air is exhausted from the air inlet and outlet holes in the second cylinder cover 7; when air is supplied to the air inlet and outlet hole in the second cylinder cover 7 and air is discharged from the air inlet and outlet hole in the first cylinder cover 6, the piston 9 moves in the reverse direction towards the second cylinder cover 7. In order to ensure the cleanliness of the air supply source in the pneumatic control assembly and ensure the normal control operation of the pneumatic control assembly, an air inlet burst device is installed on the air inlet pipeline 76 of the pneumatic control assembly. The pneumatic control assembly is positioned between the air inlet blasting device and the first cylinder cover 6.

As shown in fig. 5, the air intake burst device includes a dustproof valve assembly, a high pressure air intake pipe 18, a silencer 19, and an oil-water separator 20. As shown in fig. 7, the dust valve assembly includes a dust valve body 21 and a dust valve spool 22 that are fitted to each other. As shown in fig. 6, the high-pressure intake pipe 18, the muffler 19, and the oil-water separator 20 are respectively communicated with an inner cavity of the dustproof valve body 21. The oil-water separator 20 is in communication with the pneumatic control assembly via a pipeline. The high-pressure air inlet pipe 18 is communicated with an air supply source, and the on-off of each air passage is realized through the rotation of the dustproof valve core shaft 22 in the dustproof valve assembly. The muffler 19 can perform an effective dust removal and collection effect since gas is filtered during the operation therein.

As shown in fig. 7, a dust valve inlet channel 23 communicated with the oil-water separator 20 is further provided in the dust valve body 21, and an arc-shaped groove 24 is circumferentially provided on a side wall of the dust valve core shaft 22 located in the dust valve body 21. As shown in fig. 5, the upper end of the dust-proof valve plug shaft 22 extending out of the dust-proof valve body 21 is provided with a limit stop 25 and a handle 26, and the handle 26 can drive the limit stop 25 and the handle 26 to rotate synchronously. And a stop column 27 matched with the limit stop 25 is arranged on the dustproof valve body 21. The working state of the dust-proof valve body 21 is described with reference to fig. 5 and 7:

as shown in fig. 5 and 7, when the dustproof valve body 21 is in the closed state, the left end of the limit stop 25 contacts with the stop pillar 27, at this time, the arc-shaped groove 24 is only communicated with the muffler 19, and both the high-pressure air inlet pipe 18 and the oil-water separator 20 are blocked by the dustproof valve core shaft 22. Handle 26 is rotated clockwise, make limit stop 25's left end and bumping post 27 separation, its right-hand member is to the in-process that bumping post 27 is close to, arc 24 only with muffler 19 and high-pressure intake pipe 18 UNICOM, dustproof valve inlet channel 23 is blocked by dustproof case axle 22, at this moment, high-pressure gas gets into muffler 19 by high-pressure intake pipe 18, blow in the dust in high-pressure intake pipe 18 in muffler 19 and cross the collection, prevent that the dust from getting into pneumatic hydraulic pump assembly, thereby can prolong the life of pneumatic hydraulic pump assembly by a wide margin, this makes double-acting pneumatic hydraulic pump is fit for being more in the pit dust, and often need work under the occasion of the different high pressurized air sources of transform. When the handle 26 is continuously rotated clockwise, so that the right end of the limit stop 25 is in contact with the stop pillar 27, the arc-shaped groove 24 only enables the high-pressure air inlet pipe 18 and the dustproof valve air inlet channel 23 to be communicated with the oil-water separator 20 through the dustproof valve air inlet channel 23, the silencer 19 is blocked by the dustproof valve core shaft 22, and at the moment, high-pressure air enters the inner cavity of the cylinder barrel 8 through the pneumatic control assembly and alternately enters cavities on two sides of the piston 9, so that the piston 9 is pushed to reciprocate. From the above operation process, the air inlet blasting device has the advantages that: which does not require an additional, separate dedusting operation. The user only needs to rotate the handle 26 as usual to communicate the high-pressure air inlet pipe 18 with the oil-water separator 20, and the dust removal work of air inlet blasting can be completed in the process by the way, so that the dust removal work can be completed by the user unconsciously, and the operation is real and clean.

When a high-pressure air source needs to be provided for the pneumatic control assembly, the arc-shaped groove 24 enables the high-pressure air inlet pipe 18 to be communicated with the dustproof valve air inlet channel 23, and high-pressure air can finally enter the pneumatic control assembly through the dustproof valve air inlet channel 23 and the oil-water separator 20. Because the pneumatic control assembly and the pneumatic hydraulic pump assembly have higher requirements on the cleanness degree of the high-pressure air source, when the high-pressure air inlet pipe 18 is plugged with the air source, the position of the high-pressure air inlet pipe 18 needs to be exploded and blown to remove dust, and the operation is that the dustproof valve core shaft 22 is rotated to enable the arc-shaped groove 24 to firstly conduct the high-pressure air inlet pipe 18 and the silencer 19, so that the effect of instant explosion and blowing dust removal in communication is achieved. When the air supply of the control assembly is not needed, the arc-shaped groove 24 rotates to be only communicated with the silencer 19, and the air path of the high-pressure air inlet pipe 18 is blocked. The arrangement of the limit stop 25 and the stop column 27 limits the rotation limit position of the arc-shaped groove 24 on the dustproof valve core shaft 22, and an operator can complete the operation only by rotating the limit stop 25 to the position without additionally considering the angle problem of the required rotation of the dustproof valve core shaft 22.

Further, as shown in fig. 8, the pneumatic control assembly includes a gas circuit directional control valve 28 mounted on the first cylinder head 6, and a pneumatic valve core 29 is fittingly mounted in the gas circuit directional control valve 28. The pneumatic valve core 29 moves in the air path directional control valve 28 to form two states as shown in fig. 8 or fig. 10, the different states are connected with different air paths, and further, the reciprocating movement of the piston 9 is controlled by alternately supplying air to both sides of the piston 9. One end of the gas path directional control valve 28 is communicated with a main gas inlet connector 30, and the main gas inlet connector 30 is communicated with a gas supply source to supply gas for the gas path directional control valve 28. If an air inlet blowing device is additionally arranged, the main air inlet connector 30 is connected with the air inlet blowing device through an air inlet pipeline 76, and the air inlet blowing device is connected with a high-pressure air source for air supply. The other end of the passage switching valve 28 is provided with a pneumatic spool spring seat 3l, and the pneumatic spool spring seat 31 is provided with a pneumatic spool spring 72. The pneumatic spool spring 72 cooperates with the end of the pneumatic valve spool 29 to apply a force to the pneumatic valve spool 29 tending to move it closer to the main inlet connector 30 at all times.

As shown in fig. 8, a first cavity 32, a second cavity 33, a third cavity 34, a fourth cavity 35, a fifth cavity 36 and a spring cavity 37 are formed in the valve body of the air passage directional control valve 28. The diameters of the first cavity 32, the third cavity 34 and the fifth cavity 36 are the same, the diameters of the second cavity 33 and the fourth cavity 35 are the same, and the diameter of the first cavity 32 is smaller than that of the second cavity 33. The outer periphery of the pneumatic spool 29 is provided with a first boss 38, a second boss 39, a third boss 40, and a fourth boss 41. The first boss 38, the second boss 39, the third boss 40 and the fourth boss 41 are respectively provided with a first sealing ring 42 to ensure the air tightness among the cavities. Wherein the first boss 38, the second boss 39 and the third boss 40 have the same diameter and are all smaller than the diameter of the fourth boss 41. The third and fifth cavities 34, 36 cooperate with first, second and third bosses 38, 39, 40, and the spring cavity 37 cooperates with a fourth boss 41. The first boss 38, the second boss 39, the third boss 40, and the fourth boss 41 are all annular bosses.

As shown in fig. 9, the inner portion of the pneumatic valve core 29 is divided into an air inlet chamber 43 and a spring chamber 44, the air inlet chamber 43 and the spring chamber 44 are respectively located on both sides of the third boss 40, and a pneumatic valve core spring 72 is fitted into the spring chamber 44. A valve core air hole 45 communicated with the air inlet cavity 43 is also formed on the air-operated valve core 29 between the second boss 39 and the third boss 40. A first air passage 46 communicated with the first cavity 32, a first pump air passage 47 communicated with the second cavity 33, an exhaust port 48 communicated with the third cavity 34, a second pump air passage 49 communicated with the fourth cavity 35, and a third air passage 51 communicated with the spring cavity 37 are further formed in the valve body side wall of the air path directional control valve 28. As shown in fig. 11, the first air passage 46 and the second air passage 50 are communicated with each other through the communication hole 77. The fourth pump body air passage (55) is an air inlet and outlet hole formed in the first cylinder cover 6, and the pump body air hole 53 is an air inlet and outlet hole formed in the second cylinder cover 7.

As shown in fig. 13, a third pump body air passage 52 communicating with the first pump body air passage 47 is formed in the first cylinder head 6. As shown in fig. 16, the second cylinder head 7 has a pump body air hole 53 formed therein. As shown in fig. 3, the third pump body air passage 52 is communicated with the pump body air hole 53 through a first vent pipe 54, and the pump body air hole 53 is communicated with the inner cavity of the cylinder barrel 8. As shown in fig. 13, a fourth pump body air passage 55 communicating with the second pump body air passage 49 is also opened in the first cylinder head 6. The fourth pump body air passage 55 is communicated with the inner cavity of the cylinder barrel 8. Since the piston 9 divides the inner cavity of the cylinder 8 into two independent piston cavities, the fourth pump air passage 55 is not communicated with the pump air hole 53.

As shown in fig. 13, a fourth air passage 56 communicating with the second air passage 50 and a fifth air passage 57 communicating with the third air passage 51 are formed in the first cylinder head 6. A first mounting hole 78 is axially formed in the first cylinder head 6. The first mounting hole 78 and the second duct 50 communicate through the fourth duct 56. The first mounting hole 78 communicates with the third air passage 51 through the fifth air passage 57. Wherein, a sixth air passage 61 is arranged in the first cylinder cover 6, and the sixth air passage 61 is respectively communicated with the first mounting hole 78 and the fifth air passage 57. As shown in fig. 15, the sixth air passage 61 and the fifth air passage 57 are located on the same axial cross section of the first mounting hole 78, close to the piston 9, and are always communicated; the fourth air passage 56 is located on the other axial section of the first mounting hole 78, near the air passage directional control valve 28. The first directional control valve 58 is installed in the first installation hole 78. The first reversing control valve 58 can control the connection and disconnection between the fourth air passage 56 and the fifth air passage 57, when the first reversing control valve 58 is opened, the fourth air passage 56 and the fifth air passage 57 can be conducted through the first reversing control valve 58, and when the first reversing control valve 58 is closed, the connection between the fourth air passage 56 and the fifth air passage 57 is blocked by the first reversing control valve 58.

As shown in fig. 16, the second cylinder head 7 is provided with a second mounting hole 79 in the axial direction, and an exhaust air duct 60 and a seventh air duct 62 in the radial direction, and the exhaust air duct 60 and the seventh air duct 62 are respectively communicated with the second mounting hole 79. As shown in fig. 17, the exhaust duct 60 and the seventh duct 62 are axially aligned along the second mounting hole 79. The second direction-changing control valve 59 is installed in the second installation hole 79, and the second direction-changing control valve 59 controls the on-off of the exhaust air passage 60 and the seventh air passage 62. When the second direction-changing control valve 59 is opened, the exhaust air passage 60 and the seventh air passage 62 are communicated through the second direction-changing control valve 59, and when the second direction-changing control valve 59 is closed, the exhaust air passage 60 and the seventh air passage 62 are blocked.

As shown in fig. 4, a second communication pipe 63 is installed between the sixth air passage 6l and the seventh air passage 62.

As shown in fig. 18, when the piston 9 moves to the left to touch the first direction control valve 58, the first direction control valve 58 is opened, the fourth air passage 56 and the fifth air passage 57 are communicated, the high-pressure gas sequentially enters the fourth air passage 56 through the main gas inlet connector 30, the first cavity 32, the first air passage 46, the connecting hole 77 and the second air passage 50, then the high-pressure gas enters the spring cavity 37 through the fifth air passage 57 and the third air passage 5l through one path of the first direction control valve 58, and the other path of the high-pressure gas sequentially enters the seventh air passage 62 through the sixth air passage 61 and the second connecting pipe 63, and since the second direction control valve 59 is in a closed state, the gas in the seventh air passage 62 cannot be discharged through the exhaust air passage 60. The high-pressure gas in the spring cavity 37 acts on the fourth boss 41 and overcomes the pressure on the left side of the pneumatic valve core 29 together with the elastic force of the pneumatic valve core spring 72 to move the pneumatic valve core 29 to the left as shown in fig. 8. In this state, the fourth boss 41 is located at the end of the spring cavity 37 remote from the air-operated valve core spring seat 31, i.e., the leftmost end. The second boss 39 and the third boss 40 are located at two sides of the fourth cavity 35, the fourth cavity 35 is only communicated with the valve core air hole 45, and high-pressure gas enters the first piston cavity 80 through the main gas inlet connector 30, the gas inlet cavity 43, the valve core air hole 45, the fourth cavity 35 and the second pump body air passage 49 in sequence. The first boss 38 is located in the first cavity 32 to block the second cavity 33 from the main intake connector 30, the second cavity 33 is communicated with the exhaust port 48 through the third cavity 34, that is, the first pump air passage 47 is communicated with the exhaust port 48, and the gas in the second piston cavity 81 is discharged sequentially through the pump air hole 53, the first vent pipe 54, the third pump air passage 52, the first pump air passage 47, the second cavity 33, the third cavity 34 and the exhaust port 48. At this time, when the piston 9 moves rightward and the piston 9 moves away from the first switching control valve 58, the first switching control valve 58 is closed, and the fourth air passage 56 and the fifth air passage 57 are blocked by the first switching control valve 58. Since the high-pressure gas in the spring chamber 37 cannot be discharged through the exhaust gas passage 60 and is sealed, the pneumatic valve element 29 remains in the state shown in fig. 8.

When the piston 9 actuates the second switching control valve 59, the second switching control valve 59 is opened, and the exhaust gas passage 60 communicates with the seventh gas passage 62, as shown in fig. 19. The sixth air passage 61 is communicated with the fifth air passage 57, high-pressure air in the spring cavity 37 is discharged through the fifth air passage 57, the sixth air passage 61, the second communicating pipe 63, the seventh air passage 62 and the exhaust air passage 60 in sequence, at this time, the pressure at the left end of the air-operated valve core 29 overcomes the elastic force of the air-operated valve core spring 72 to push the air-operated valve core 29 to move to the right to move to the position shown in fig. 10, the fourth boss 41 is positioned at one end, close to the air-operated valve core spring seat 31, in the spring cavity 37, the second boss 39 and the third boss 40 are positioned in the fifth cavity 36, and the valve core air hole 45 is blocked. The first boss 38 is located in the third cavity 34, the first cavity 32 is communicated with the second cavity 33, and the high-pressure gas can enter the second piston cavity 81 through the first cavity 32, the second cavity 33, the first pump air passage 47, the third pump air passage 52, the first vent pipe 54 and the pump air holes 53 in sequence. The second pump body air passage 49 is communicated with the exhaust port 48, and the gas in the first piston cavity 80 can be discharged through the fourth pump body air passage 55, the second pump body air passage 49, the fourth cavity 35 and the exhaust port 48 in sequence. At this time, the piston 9 moves leftward and moves away from the second directional control valve 59, the second directional control valve 59 is closed, and the exhaust air passage 60 and the seventh air passage 62 are blocked.

The communication of the air passages and the action of the pneumatic valve core 29 are described in detail below with reference to the moving position of the piston 9: regardless of the state of the pneumatic valve 29, the first air passage 46 is always communicated with the main air inlet connector 30, and the first air passage 46 and the second air passage 50 are always filled with high-pressure air.

The first process is as follows: when the piston 9 moves closer to the first cylinder head 6 to contact the first directional control valve 58, as shown in fig. 18, the fourth air passage 56 and the fifth air passage 57 are communicated, the exhaust air passage 60 and the seventh air passage 62 are not communicated, the high-pressure air in the second air passage 50 sequentially enters the spring cavity 37 through the fourth air passage 56, the fifth air passage 57 and the third air passage 51, and pushes the fourth boss 41 to move instantaneously to the state shown in fig. 8, at this time, a part of the high-pressure air in the main intake connector 30 still enters the first air passage 46, and another part of the high-pressure air enters the fourth pump body air passage 55 on the first cylinder head 6 through the intake chamber 43, the spool air hole 45, the fourth cavity 35 and the second pump body air passage 49, and then the high-pressure air pushes the piston 9 to approach the second cylinder head 7. When the first switching control valve 58 is out of contact, the fourth air passage 56 and the fifth air passage 57 are not communicated.

And a second process: in the process before the piston 9 approaches the second cylinder head 7 and does not contact the second directional control valve 59, when the piston 9 moves to the right, the gas in the second piston cavity 81 is compressed into the pump body air hole 53 and is discharged through the first vent pipe 54, the third pump body air passage 52, the first pump body air passage 47, the second cavity 33, the third cavity 34 and the exhaust port 48 in sequence. Since the exhaust gas passage 60 is not in contact with the second switching control valve 59, the seventh gas passage 62 is not communicated with the exhaust gas passage 60, and the high-pressure gas in the spring chamber 37 is not discharged through the exhaust gas passage 60, and the pneumatic valve spool 29 maintains the state shown in fig. 8.

The third process: when the piston 9 moves closer to the second cylinder head 7 to contact the second directional control valve 59, as shown in fig. 19, the exhaust air passage 60 communicates with the seventh air passage 62, the high-pressure air in the spring cavity 37 can be exhausted through the third air passage 51, the fifth air passage 57, the sixth air passage 61, the second communicating pipe 63, the seventh air passage 62 and the exhaust air passage 60 in sequence, the pneumatic spool 29 moves right to the state shown in fig. 10 instantly, at this time, a part of the high-pressure air in the main intake connector 30 still enters the first air passage 46, because the spool air hole 45 is completely blocked in the fifth cavity 36, and another part of the high-pressure air enters the inner side of the second cylinder head 7 through the second cavity 33, the first pump body air passage 47, the third pump body air passage 52, the first air passage 54 and the pump body air hole 53, and then the high-pressure air pushes the piston 9 to move closer to the position of the first cylinder head 6.

The process four is as follows: when the piston 9 moves leftward while approaching the first cylinder head 6 and before contacting the first directional control valve 58, the gas in the first piston chamber 80 is compressed into the fourth cylinder gas passage 55, and is discharged through the second cylinder gas passage 49, the fourth chamber 35, the third chamber 34, and the exhaust port 48 in this order. Since the fourth air passage 56 and the fifth air passage 57 are not in contact with the first direction switching control valve 58, no high-pressure air is filled in the spring cavity 37, and under the condition that air is continuously supplied from the air supply source, pressure is always applied to the third boss 40 and the pneumatic valve core 29 at the rear end, and the pneumatic valve core 29 maintains the state shown in fig. 10 in the process.

Until the piston 9 moves towards the first cylinder cover 6 to be contacted with the first reversing control valve 58, the first reversing control valve returns to the state of the first process, so that a cycle is formed, and the function of controlling the reciprocating movement and reversing of the piston 9 by the pneumatic control assembly is achieved.

Further, in order to ensure normal exhaust during the reciprocating movement of the piston 9, two pump body air holes 53 are formed in the inner side of the second cylinder cover 7, and the third pump body air passage 52 is divided into two paths and is respectively communicated with the pump body air holes 53 through a first air pipe 54.

Further, as shown in fig. 20, the first direction control valve 58 includes a first direction valve spring seat 64 installed outside the first cylinder head 6 and a first direction control valve sleeve 65 installed inside the first cylinder head 6. The inner end of the first reversing control valve sleeve 65 is provided with a vent cavity 651, the side wall of the vent cavity 651 is provided with a plurality of vent holes 650, one vent hole 650 is communicated with the sixth air channel 61, the other vent hole 650 is communicated with the fifth air channel 57, and the vent holes 650 and the vent cavity 651 ensure that the fifth air channel 57 is communicated with the sixth air channel 61 all the time. The first direction control valve sleeve 65 is internally provided with a first control valve core 66 in a matching way, the periphery of the first control valve core 66 is provided with a second sealing ring 82, and the second sealing ring 82 can seal the fourth air channel 56. The end of the first control valve spool 66 extends through the first direction control valve sleeve 65 and is positioned within the cylinder barrel 8. A first direction valve spring 67 is installed between the first control valve spool 66 and the first direction valve spring seat 64. The first direction valve spring 67 always tends to close the fourth gas passage 56 with the first control valve spool 66. The fifth air passage 57 and the sixth air passage 61 are always communicated through the first direction change control valve sleeve 65. When the piston 9 pushes the first control valve core 66 to move leftward against the elastic force of the first direction valve spring 67, the fourth air duct 56 can be communicated with the vent cavity 651, that is, the fourth air duct 56 is communicated with the fifth air duct 57, so as to implement the air path control direction changing function.

Further, as shown in fig. 21, the second direction switching control valve 59 may have the same structure as the first direction switching control valve 58 except that the installation position is opposite thereto. The air cylinder comprises a second reversing valve spring seat 68 arranged on the outer side of the second cylinder cover 7 and a second reversing control valve sleeve 69 arranged on the inner side of the second cylinder cover 7, wherein a second control valve spool 70 is arranged in the second reversing control valve sleeve 69 in a matched mode, the end portion of the second control valve spool 70 penetrates through the second reversing control valve sleeve 69 and is located in the cylinder barrel 8, a second reversing valve spring 71 is arranged between the second control valve spool 70 and the second reversing valve spring seat 68, the second reversing valve spring 71 always tends to seal the seventh air channel 62, and the exhaust air channel 60 is communicated with the second reversing control valve sleeve 69. When the piston 9 moves close to the second direction control valve 59 and overcomes the elastic force of the second direction valve spring 71 to push the second control valve core 70 to move, the seventh air passage 62 can be communicated with the second direction control valve sleeve 69, that is, the seventh air passage 62 is communicated with the exhaust air passage 60, so as to realize the air passage control direction changing function.

The technical solution of the present invention is not limited to the scope of the embodiments of the present invention. The technical contents not described in detail in the present invention are all known techniques.