Novel portable gas-driven hydraulic pump for emergency rescue

Abstract

According to the novel portable air-driven hydraulic pump for emergency rescue, a vane type pneumatic motor is adopted to directly drive a plunger pump, the flow direction of compressed air is controlled through an integrated pneumatic control valve, vanes are driven to rotate in the forward direction or the reverse direction, a rotating shaft and a plunger sleeve are driven to rotate, and a plunger moves in a reciprocating mode under the action of a swash plate; and stable output of hydraulic oil is achieved. Compared with a traditional gas-driven hydraulic pump, the rotary blade motor replaces a reciprocating motion air cylinder, the problems of large vibration and high noise are solved, and the use requirements of open type, semi-closed type and closed type hydraulic systems can be met. The size and weight of equipment are reduced through the compact integrated design, the integrated pneumatic control valve can achieve dynamic adjustment of the flow and direction of an oil source, stability of hydraulic output is ensured through cooperative work of multiple plungers, the double advantages of anti-explosion and high-pressure output are achieved, and the hydraulic control device is particularly suitable for being used in anti-explosion places such as coal mines and chemical engineering and special operation environments such as underwater rescue. And a lightweight and portable power solution is provided for emergency rescue.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of hydraulic pumps, and particularly relates to a novel portable air-driven hydraulic pump for emergency rescue. BACKGROUND

[0002] In fire rescue, natural disaster rescue and production accident emergency treatment, especially in coal mines, chemical industry, underwater and other explosion-proof or special environments, rescue equipment needs to meet the requirements of high efficiency, portability, safety and reliability. Such rescue operations often require the use of hydraulic rescue tools such as shearing pliers and dilators to complete key operations such as breaking and jacking. The power source of these tools mainly relies on hydraulic drive systems. Hydraulic drive technology can provide powerful power output and precise motion control for rescue tools due to its high power density and precise control, which makes hydraulic drive system the preferred power solution for modern emergency rescue equipment.

[0003] As the core component of the hydraulic drive system, the performance of the hydraulic pump directly determines the power output characteristics of the entire system. The hydraulic pump is connected to the oil tank, and low-pressure hydraulic oil is sucked from the oil tank. After the pressurization of the mechanical structure in the pump, high-pressure oil is delivered to the actuator (such as hydraulic cylinder or hydraulic motor) of the hydraulic system, thereby driving the actuator to complete the predetermined action. This "suction-pressurization-output" working cycle makes the hydraulic pump a key link connecting energy supply and actuator.

[0004] At present, the hydraulic pump applied to rescue equipment mainly uses a manual pump or an electric pump as a power source, but in actual rescue scenarios, both power supply methods have obvious shortcomings. Although the manual hydraulic pump is simple in structure and does not require external energy, it completely relies on manual operation, which limits its output flow and pressure, and makes it difficult to adapt to long-distance or long-time continuous operation; although the electric hydraulic pump can provide stable power output, it has the risk of electric spark in flammable and explosive environments, and needs to be matched with a power supply, which seriously limits its application in special occasions.

[0005] To solve the above problems, air-driven hydraulic pumps have gradually become a research hotspot. This kind of pump uses compressed air to drive the hydraulic pump, and through the conversion of air pressure into mechanical energy, it drives the hydraulic pump to work, which not only retains the high pressure characteristics of the hydraulic system, but also has the explosion-proof advantage of the pneumatic system. However, the existing air-driven hydraulic pump adopts the structural design of a large-section air cylinder driving a small-diameter single-plunger pump. The reciprocating motion of the air cylinder drives the reciprocating motion of the plunger of the single-plunger pump. When the plunger retracts, the volume of the pump cavity increases, and oil is sucked from the oil tank. When the plunger extends, the oil is compressed, and high-pressure oil is output to the actuator, that is, the reciprocating motion of the air cylinder realizes pressure increase. The reciprocating motion of the air cylinder causes severe vibration of the equipment and excessive noise, and the intermittent oil discharge of the single-plunger pump causes obvious hydraulic pulsation, affecting the stability of the actuator. In addition, the stroke of the traditional reciprocating air-driven pump is long, and in order to realize the reciprocating motion of the air cylinder, an additional reversing component such as a reversing valve needs to be configured at the rear end of the equipment, making the structure of the entire hydraulic pump cumbersome and bulky, which is not conducive to rapid deployment and portable use, and it is difficult to meet the strict requirements of emergency rescue equipment for lightweight and compactness.

[0006] With the increasing complexity of emergency rescue scenes, especially in special environments such as explosion-proof and underwater, higher requirements are put forward for rescue equipment. How to realize efficient integration of air-driven hydraulic pumps, while ensuring power output, improving running stability and reducing equipment size, has become a technical problem to be solved in the field. Developing a compact, stable and portable air-driven hydraulic pump is of great significance to improve the efficiency of rescue in special environments. SUMMARY

[0007] The purpose of the present application is to provide a new type of portable air-driven hydraulic pump for emergency rescue, to solve the technical problems of the existing air-driven hydraulic pump, such as large equipment vibration, high noise, bulky volume, and obvious hydraulic pulsation of single-plunger pump, caused by the reciprocating motion of the air cylinder.

[0008] The technical problems solved by the present application can be realized by the following scheme: A new type of portable air-driven hydraulic pump for emergency rescue, comprising: A vane-type pneumatic motor has a pneumatic motor housing, a cylinder sleeve is fixed in the pneumatic motor housing, a rotating shaft is arranged in the cylinder sleeve, a plurality of vanes are installed on the rotating shaft, an air inlet flow distribution disc and an air outlet flow distribution disc are fixed on both sides of the cylinder sleeve; An air control valve is integrated on the pneumatic motor housing and can communicate with the air inlet on the air inlet flow distribution disc and the air outlet on the air outlet flow distribution disc; The plunger pump comprises a plunger pump housing, a plunger sleeve arranged in the plunger pump housing, a plurality of plungers slidingly arranged in the plunger sleeve, and a swash plate fixed in the plunger pump housing; a plunger pre-tightening spring is arranged between the plunger sleeve and the plunger to ensure that the plunger is always in contact with the swash plate; and the plunger sleeve is keyed to a rotating shaft of a vane-type pneumatic motor. The air control valve controls compressed air to enter the cylinder sleeve through the air inlet of the air inlet flow distribution disc, drives the vane to rotate, and further drives the rotating shaft and the plunger sleeve to rotate, so that the plunger reciprocates under the action of the swash plate to realize the suction and pressurized output of hydraulic oil.

[0009] Further, the pneumatic motor housing is provided with a housing forward rotation flow channel and a housing reverse rotation flow channel which can communicate with the air supply channel of the air control valve. The air inlet flow distribution disc is provided with a forward rotation air inlet and a reverse rotation air inlet which communicate with the housing forward rotation flow channel and the housing reverse rotation flow channel respectively, and the exhaust flow distribution disc is provided with a forward rotation exhaust outlet and a reverse rotation exhaust outlet which communicate with the forward rotation air inlet and the reverse rotation air inlet respectively.

[0010] Further, the air control valve is a three-position air control valve with a forward rotation position, a reverse rotation position and a neutral position. When the air control valve is in the forward rotation position, the air supply channel thereof communicates with the housing forward rotation flow channel of the pneumatic motor housing, compressed air enters the cylinder sleeve through the housing forward rotation flow channel and the forward rotation air inlet of the air inlet flow distribution disc, and can be discharged through the forward rotation exhaust outlet of the exhaust flow distribution disc to drive the vane and the rotating shaft to rotate forward. When the air control valve is in the reverse rotation position, the air supply channel thereof communicates with the housing reverse rotation flow channel of the pneumatic motor housing, compressed air enters the cylinder sleeve through the housing reverse rotation flow channel and the reverse rotation air inlet of the air inlet flow distribution disc, and can be discharged through the reverse rotation exhaust outlet of the exhaust flow distribution disc to drive the vane and the rotating shaft to rotate reversely.

[0011] Further, the cylinder sleeve is provided with a through-type cylinder sleeve forward rotation flow channel and a cylinder sleeve reverse rotation flow channel in the axial direction, the cylinder sleeve forward rotation flow channel communicates the forward rotation air inlet of the air inlet flow distribution disc and the forward rotation exhaust outlet of the exhaust flow distribution disc, and the cylinder sleeve reverse rotation flow channel communicates the reverse rotation air inlet of the air inlet flow distribution disc and the reverse rotation exhaust outlet of the exhaust flow distribution disc. Compressed air can enter the cylinder sleeve through the housing forward rotation flow channel, the forward rotation air inlet of the air inlet flow distribution disc and the cylinder sleeve forward rotation flow channel, and can be discharged through the forward rotation exhaust outlet of the exhaust flow distribution disc to drive the vane and the rotating shaft to rotate forward. Compressed air can enter the cylinder sleeve through the housing reverse rotation flow channel, the reverse rotation air inlet of the air inlet flow distribution disc and the cylinder sleeve reverse rotation flow channel, and can be discharged through the reverse rotation exhaust outlet of the exhaust flow distribution disc to drive the vane and the rotating shaft to rotate reversely.

[0012] Further: the two ends of the cylinder sleeve forward flow channel and the cylinder sleeve reverse flow channel are provided with exhaust grooves which are communicated with the cylinder sleeve forward flow channel and the cylinder sleeve reverse flow channel, the exhaust grooves are communicated with the inside of the cylinder sleeve, and compressed air can enter the cavity between adjacent blades in the cylinder sleeve through the exhaust grooves to push the blades to rotate.

[0013] Further: the cylinder sleeve is an eccentric cylinder sleeve, the inner hole of the cylinder sleeve is eccentric with the rotating shaft, a plurality of rotating shaft grooves are formed on the rotating shaft, and the blades are slidingly installed in the rotating shaft grooves. A first blade radial thrust flow channel which is communicated with the forward intake port or the reverse intake port is formed on the intake flow distribution disc, a second blade radial thrust flow channel which is communicated with the forward exhaust port or the reverse exhaust port is formed on the exhaust flow distribution disc, and compressed air can enter the gap between the blades and the rotating shaft grooves through the first blade radial thrust flow channel and the second blade radial thrust flow channel to push the blades to press against the inner wall of the cylinder sleeve.

[0014] Further: a main exhaust port which is communicated with the forward exhaust port and the reverse exhaust port on the exhaust flow distribution disc is formed on the cylinder sleeve, a secondary exhaust port which is communicated with the main exhaust port is formed on the pneumatic motor shell, a silencer which is connected with the secondary exhaust port is fixed on the pneumatic motor shell, and compressed air is discharged through the silencer after passing through the main exhaust port and the secondary exhaust port.

[0015] Further: the plunger pump shell is fixedly installed on the pneumatic motor shell, a disc spring is arranged between the plunger pump shell and the exhaust flow distribution disc, the disc spring generates an axial compression force, and the exhaust flow distribution disc, the cylinder sleeve and the intake flow distribution disc are kept in a closely adhered state. Positioning pin holes which correspond in position are formed on the exhaust flow distribution disc, the cylinder sleeve, the intake flow distribution disc and the pneumatic motor shell, and a positioning pin sequentially penetrates through the positioning pin holes of the exhaust flow distribution disc, the cylinder sleeve, the intake flow distribution disc and the pneumatic motor shell to position the components.

[0016] Further: the end of the plunger away from the plunger pre-tightening spring is a spherical end, a sliding shoe which can slidingly contact the swash plate is hinged to the spherical end, a return disc is fixed to the side of the sliding shoe which does not contact the swash plate, a return disc positioning sleeve is sleeved on the rotating shaft, and a return disc compression spring is arranged between the return disc positioning sleeve and the plunger sleeve.

[0017] Further: a plunger pump flow distribution block is fixedly installed on the plunger pump shell, and an oil supplementing balance valve is integrated in the plunger pump flow distribution block. The first distribution block oil channel and the second distribution block oil channel are provided in the plunger pump distribution block, first hydraulic oil inlet and outlet holes and second hydraulic oil inlet and outlet holes are respectively provided in the first distribution block oil channel and the second distribution block oil channel, the first hydraulic oil inlet and outlet holes and the second hydraulic oil inlet and outlet holes are communicated with the plunger pump cavity through first distribution channels and second distribution channels provided on the plunger pump distribution block, the first hydraulic oil inlet and outlet holes and the second hydraulic oil inlet and outlet holes can be communicated with the rodless cavity of the hydraulic cylinder and the rod cavity of the hydraulic cylinder respectively, an oil return and oil supplement channel communicated with the first distribution block oil channel and the second distribution block oil channel is provided in the plunger pump distribution block, an oil return and oil supplement valve is installed in the oil return and oil supplement channel, an oil return and oil supplement opening communicated with the oil return and oil supplement channel is provided on the oil return and oil supplement channel, and the oil return and oil supplement opening can be communicated with an oil tank.

[0018] Further, the oil return and oil supplement valve comprises a sliding valve spool slidingly installed in the oil return and oil supplement channel, the sliding valve spool comprises a valve rod and first and second valve blocks fixedly installed on the valve rod and arranged at a certain interval, a oil return and oil supplement valve opening communicated with the oil return and oil supplement opening is formed between the first and second valve blocks, the opening of the oil return and oil supplement channel is closed by a plug, a first return spring is arranged between the first valve block and the oil return and oil supplement channel, and a second return spring is arranged between the second valve block and the plug. When the pressure on one side of the first distribution block oil channel is greater than the pressure on one side of the second distribution block oil channel, the sliding valve spool moves towards the second distribution block oil channel to make the oil return and oil supplement valve opening communicated with the second distribution block oil channel, and when the pressure on one side of the second distribution block oil channel is greater than the pressure on one side of the first distribution block oil channel, the sliding valve spool moves towards the first distribution block oil channel to make the oil return and oil supplement valve opening communicated with the first distribution block oil channel.

[0019] The novel portable air-driven hydraulic pump for emergency rescue of the application effectively solves the technical problems existing in the application of the traditional rescue hydraulic pump in special environments through innovative structural design. The integrated structure of the vane air motor directly driving the plunger pump discards the heavy cylinder reciprocating mechanism and the complex reversing valve system in the traditional air-driven hydraulic pump, significantly reduces the overall equipment volume and weight, and meets the requirement of equipment portability for emergency rescue. The continuous rotary motion of the vane motor replaces the reciprocating motion of the traditional cylinder, fundamentally eliminates the vibration and impact caused by mechanical reversing, significantly improves the equipment running stability, and significantly reduces the noise level.

[0020] The unique swash plate type plunger pump design cooperates with multiple plungers to work together to realize continuous and stable output of hydraulic oil, effectively overcomes the hydraulic pulsation problem caused by intermittent oil discharge of single plunger pumps, and ensures the stability and accuracy of the actuator action. The integrated air control valve design not only simplifies the air inlet control of the motor, making the operation more convenient, but also further optimizes the overall structural layout, improves the compactness and portability of the equipment.

[0021] The present application solves the technical problems of large volume, strong vibration, and obvious hydraulic pulsation of the traditional gas-driven hydraulic pump by integrating the vane-type pneumatic motor and the plunger pump into a one-piece structure. The design fully utilizes the advantages of explosion-proof safety of the pneumatic system and high-pressure output of the hydraulic system. The structure of the rotating vane motor directly driving the plunger pump not only completely eliminates the vibration and noise problems caused by the reciprocating motion of the traditional cylinder, but also simplifies the overall structural layout. The compact integrated design significantly reduces the volume and weight of the device, and the coordinated work of multiple plungers ensures the smooth output of hydraulic oil. This innovative power conversion scheme enables the device to maintain high-pressure performance while achieving lightweight, portability, and stable operation, providing a safe and reliable power solution for explosion-proof environments such as coal mines, chemical plants, and special operating environments such as underwater rescue. BRIEF DESCRIPTION OF DRAWINGS

[0022] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the following will briefly introduce the drawings needed to be used in the embodiment description. Obviously, the drawings in the following description are only some embodiments of the present application, and other drawings can also be obtained by those skilled in the art without creative labor.

[0023] Figure 1 is a front view structural schematic diagram of a novel portable gas-driven hydraulic pump for emergency rescue according to the first embodiment of the present application; Figure 2 is a sectional view structural schematic diagram of a novel portable gas-driven hydraulic pump for emergency rescue according to the first embodiment of the present application; Figure 3 is a left view of an air inlet flow distribution disc of a novel portable gas-driven hydraulic pump for emergency rescue according to the first embodiment of the present application; Figure 4 is a right view of an air outlet flow distribution disc of a novel portable gas-driven hydraulic pump for emergency rescue according to the first embodiment of the present application; Figure 5 is a sectional view along the A-A direction of Figure 2 ; Figure 6 is an enlarged view of part B of Figure 2 ; Figure 7 is a sectional view along the C-C direction of Figure 2 ; Figure 8 is a right view of a cylinder sleeve of a novel portable gas-driven hydraulic pump for emergency rescue according to the first embodiment of the present application; Figure 9This is a schematic diagram of the three-dimensional structure of a cylinder sleeve of a novel portable air-driven hydraulic pump for emergency rescue, as viewed from the left, in accordance with a first embodiment of the present invention; Figure 10 This is a schematic cross-sectional view of a novel portable air-driven hydraulic pump for emergency rescue according to a second specific embodiment of the present invention; Figure 11 It is along Figure 10 Cross-sectional view in DD direction; Figure 12 yes Figure 11 A local enlarged view of point E; Figure 13 This is a right side view of a plunger pump manifold block of a novel portable air-driven hydraulic pump for emergency rescue according to a second specific embodiment of the present invention; Figure 14 This is a structural diagram of a novel portable air-driven hydraulic pump for emergency rescue used in a semi-closed hydraulic system according to a second specific embodiment of the present invention; Figure 15 This is a structural diagram of a novel portable air-driven hydraulic pump for emergency rescue used in a closed hydraulic system according to a second specific embodiment of the present invention; Main parts and numbers: Vane-type pneumatic motor: 1; pneumatic motor housing: 11; housing forward flow channel: 111; housing reverse flow channel: 112; auxiliary exhaust port: 113; muffler: 114; housing air inlet: 115; cylinder liner: 12; cylinder liner forward flow channel: 121; cylinder liner reverse flow channel: 122; first exhaust groove: 123; second exhaust groove: 124; main exhaust port: 125; rotating shaft: 13; rotating shaft groove: 131; blade: 14; air intake manifold: 15; forward air inlet: 151; reverse air inlet: 152; first blade radial thrust flow channel: 153; exhaust manifold: 16; forward exhaust port: 161; reverse exhaust port: 162; second blade radial thrust flow channel: 163; disc spring: 171; positioning pin: 172; Air control valve: 2; air supply channel: 21; air control valve core: 22; blocking block: 23; spring pin: 24; Plunger pump: 3; Plunger pump housing: 31; Plunger pump oil suction channel: 311; Plunger sleeve: 32; Needle roller bearing: 321; Plunger: 33; Swash plate: 34; Plunger preload spring: 351; Slipper: 352; Return plate: 353; Return plate positioning sleeve: 354; Return plate pressure spring: 355; Piston pump distribution block: 4; first distribution block oil passage: 41; first hydraulic oil inlet and outlet hole: 411; second distribution block oil passage: 42; second hydraulic oil inlet and outlet hole: 421; first distribution channel: 431; second distribution channel: 432; return oil replenishment channel: 44; return oil replenishment port: 441; filter element: 45; Oil compensation balance valve: 5; spool valve core: 51; valve stem: 511; first valve block: 512; second valve block: 513; oil compensation balance valve port: 514; plug: 52; first return spring: 531; second return spring: 532; Oil tank: 600; Hydraulic cylinder: 710; emergency rescue tool: 720; Oil bag: 800. DETAILED DESCRIPTION

[0024] In order to make the purpose, technical scheme and advantages of the present application more clearly, the embodiments of the present application will be further described in detail below with reference to the drawings.

[0025] DETAILED DESCRIPTION Figure 1 、 2 A structure diagram of a new type of portable air-driven hydraulic pump for emergency rescue is shown in the present embodiment, as shown in the figure, the air-driven hydraulic pump comprises a vane air motor 1, a gas control valve 2 integrated on the vane air motor 1, and a plunger pump 3 connected with the vane air motor 1 and driven by the vane air motor 1, as shown in the figure, the vane air motor 1 comprises an air motor shell 11, a cylinder sleeve 12 is fixed in the air motor shell 11, a rotatable rotating shaft 13 is rotatably installed in the cylinder sleeve 12, a plurality of vanes 14 are installed on the rotating shaft 13, the vanes 14 rotate to drive the rotating shaft 13 to rotate, an air inlet distribution disc 15 and an air outlet distribution disc 16 are respectively fixed on both sides of the cylinder sleeve 12, as shown in the figure, the air inlet distribution disc 15 is provided with a forward rotation air inlet 151 and a reverse rotation air inlet 152, as shown in the figure, the air outlet distribution disc 16 is provided with a forward rotation air outlet 161 and a reverse rotation air outlet 162. Figure 1 Figure 2 Figure 3 Figure 4 The gas control valve 2 is integrated on the air motor shell 11, a gas supply channel 21 (shown in the figure) of the gas control valve 2 can communicate with the forward rotation air inlet 151 or the reverse rotation air inlet 152 on the air inlet distribution disc 15, the forward rotation air inlet 151 on the air inlet distribution disc 15 communicates with the forward rotation air outlet 161 on the air outlet distribution disc 16, and the reverse rotation air inlet 152 communicates with the reverse rotation air outlet 162 on the air outlet distribution disc 16.

[0026] The gas control valve 2 is integrated on the air motor shell 11, a gas supply channel 21 (shown in the figure) of the gas control valve 2 can communicate with the forward rotation air inlet 151 or the reverse rotation air inlet 152 on the air inlet distribution disc 15, the forward rotation air inlet 151 on the air inlet distribution disc 15 communicates with the forward rotation air outlet 161 on the air outlet distribution disc 16, and the reverse rotation air inlet 152 communicates with the reverse rotation air outlet 162 on the air outlet distribution disc 16. Figure 5

[0027] Figure 6 ​​​​​As shown, the plunger pump 3 comprises a plunger pump housing 31 fixed on the pneumatic motor housing 11, a plunger sleeve 32 is rotatably installed in the plunger pump housing 31, a needle bearing 321 is externally sleeved on the plunger sleeve 32 for limiting the radial movement of the plunger sleeve 32 and preventing vibration and deflection problems caused by cantilever installation. A plurality of sliding grooves are formed in the plunger sleeve 32 in the circumferential direction, and a plunger 33 is slidably installed in each sliding groove. The axial direction of the plunger 33 is parallel to the axial direction of the plunger sleeve 32. A swash plate 34 is fixedly installed in the plunger pump housing 31. As shown, Figure 6 The working surface of the swash plate 34 is an inclined surface that is inclined at a certain angle with respect to the axis of the plunger 33. A plunger pre-tightening spring 351 is arranged between the plunger sleeve 32 and the plunger 33. The elastic force of the plunger pre-tightening spring 351 presses the plunger 33 against the inclined surface of the swash plate 34, so that the plunger 33 is always in contact with the inclined surface of the swash plate 34. The plunger sleeve 32 is keyed connected with the rotating shaft 13 of the vane-type pneumatic motor 1. When the rotating shaft 13 rotates, it drives the plunger sleeve 32 to rotate. When the plunger sleeve 32 rotates, it drives the plunger 33 to rotate around the axis of the plunger sleeve 32. Under the action of the inclined surface of the swash plate 34, the plunger 33 rotates while making axial reciprocating extension and retraction in the sliding groove of the plunger sleeve 32. The plunger pump 3 can be connected in communication with an oil tank (not shown in the drawings) storing hydraulic oil through an oil passage. The plunger pump 3 can be connected with an actuator such as a hydraulic cylinder (not shown in the drawings) through an oil passage.

[0028] The compressed air enters the forward rotation inlet port 151 or the reverse rotation inlet port 152 of the inlet distribution disc 15 through the air supply passage 21 of the air control valve 2, and then enters the cylinder sleeve 12 through the inlet port, pushes the vane 14 to rotate forward or reverse, and in turn drives the rotating shaft 13 and the plunger sleeve 32 to rotate forward or reverse. The rotation of the plunger sleeve 32 drives the plunger 33 to rotate, and under the action of the inclined surface of the swash plate 34, the plunger 33 rotates while making reciprocating motion, so as to realize the suction and pressurized output of hydraulic oil.

[0029] When the air-driven hydraulic pump of this embodiment is working, the compressed air enters the forward air inlet 151 or the reverse air inlet 152 of the air intake distribution plate 15 through the air supply channel 21 of the air control valve 2, and enters the cylinder sleeve 12 after distribution to push the blade 14 to rotate, thereby driving the rotating shaft 13 and the plunger sleeve 32 keyed thereto to rotate synchronously; the plunger 33 always keeps in contact with the inclined surface of the swash plate 34 under the action of the plunger preload spring 351, and as the plunger sleeve 32 rotates, multiple plungers 33 are moved in phase difference under the action of the inclined surface of the swash plate 34. The pistons 33 perform reciprocating motions in sequence. When one piston 33 moves toward the swash plate 34, the volume of the corresponding pump chamber increases, creating negative pressure and sucking hydraulic oil from the oil tank. At the same time, another piston 33 is in the stage of moving away from the swash plate 34, compressing the hydraulic oil in its pump chamber to form a high-pressure output. The alternating operation of the multiple pistons 33 ensures a continuous connection between the oil suction and oil compression processes, ensuring the continuity of the hydraulic oil output. The compressed air after operation is discharged through the forward exhaust port 161 or the reverse exhaust port 162 of the exhaust manifold 16. The air intake direction can be adjusted by controlling the air control valve 2, thereby controlling the rotation direction of the vane-type pneumatic motor 1. During the entire process, the rotational motion of the vane-type pneumatic motor 1 is directly converted into the reciprocating motion of the pistons 33, eliminating the cylinder reciprocating mechanism and reversing components in traditional air-driven hydraulic pumps, making energy transfer more efficient and direct. The alternating operation of the multiple pistons 33 ensures the continuous and stable output of hydraulic oil, while the integrated air control valve design and compact structural layout reduce the overall volume, achieving the design goal of portability.

[0030] In order to realize the forward and reverse rotation of the vane type air motor 1, Figure 5 As shown, the pneumatic motor housing 11 is provided with a housing forward flow channel 111 and a housing reverse flow channel 112 that are capable of communicating with the air supply channel 21 of the air control valve 2. The forward air inlet 151 provided on the air intake manifold 15 is in communication with the housing forward flow channel 111, and the reverse air inlet 152 is in communication with the housing reverse flow channel 112. The forward exhaust port 161 provided on the exhaust manifold 16 is in communication with the forward air inlet 151 of the air intake manifold 15, and the reverse exhaust port 162 is in communication with the reverse air inlet 152.

[0031] The air control valve 2 is a three-position air control valve having a forward rotation position, a reverse rotation position, and a neutral stop position. When the air control valve 2 is in the forward rotation position, its air supply channel 21 communicates with the forward rotation flow channel 111 of the pneumatic motor housing 11. Compressed air flows through the air supply channel 21 of the air control valve 2, the forward rotation flow channel 111, and the forward rotation air inlet 151 of the air intake manifold 15 into the cylinder liner 12, and can be discharged through the forward rotation exhaust port 161 of the exhaust manifold 16, thereby driving the blades 14, the rotating shaft 13, and the plunger sleeve 32 to rotate in the forward direction. When the air control valve 2 is in the reverse position, its air supply passage 21 communicates with the reverse flow passage 112 of the pneumatic motor housing 11. Compressed air flows through the air supply passage 21 of the air control valve 2, the reverse flow passage 112, and the reverse air inlet 152 of the air intake manifold 15 into the cylinder liner 12, and can be discharged through the reverse exhaust port 162 of the exhaust manifold 16, thereby driving the vanes 14, the rotating shaft 13, and the plunger sleeve 32 to rotate in the opposite direction. When the air control valve 2 is in the neutral stop position, the compressed air supply is blocked, the vanes 14 stop rotating, and the vane-type pneumatic motor 1 stops operating.

[0032] To realize the switching control of the air control valve 2 between the forward rotation position, reverse position and the middle stop position, as shown in FIG. Figure 5 As shown, the air control valve 2 includes an air control valve core 22, which is slidably installed in the mounting hole of the pneumatic motor housing 11. The axial direction of the mounting hole is perpendicular to the axial direction of the vane-type pneumatic motor 1, and the mounting hole is communicated with the housing air inlet 115 opened on the pneumatic motor housing 11. A block 23 is fixedly provided in the middle of the air control valve core 22, and two air supply channels 21 are formed between the outer surface of the air control valve core 22 and the inner wall of the mounting hole of the pneumatic motor housing 11. The two air supply channels 21 are located on both sides of the block 23, one of the air supply channels 21 is close to the housing forward flow channel 111 and can be connected to the housing forward flow channel 111, and the other air supply channel 21 is close to the housing reverse flow channel 112 and can be connected to the housing reverse flow channel 112. An installation groove is provided on the air control valve core 22, in which a spring pin 24 is installed for locking the position of the air control valve core 22. The spring pin 24 adopts a conventional existing spring pin, including a spring and a locking ball. The spring is installed between the locking ball and the air control valve core 22. The locking ball is pressed into the locking groove provided on the pneumatic motor housing 11 by the spring preload force, thereby locking the position of the air control valve core 22.

[0033] When the air control valve 2 is in the middle stop position ( Figure 5 The middle air control valve 2 is in its neutral stop position. The locking ball of the spring pin 24 is engaged in the locking groove on the pneumatic motor housing 11 under the preload of the spring, so that the air control valve core 22 remains in a fixed position. At this time, the blocking block 23 closes the housing air inlet 115, and both air supply channels 21 are blocked, and the vane-type pneumatic motor 1 stops working.

[0034] When the vane-type pneumatic motor 1 needs to work in the forward direction, the air control valve core 22 moves from the middle stop position toward the housing reverse flow channel 112 (ie, toward the reverse direction). Figure 5 The air control valve 2 is in the forward rotation position, and the air supply channel 21 of the air control valve 2 is close to the forward rotation channel 111 of the shell, and the compressed air enters the forward rotation channel 111 of the shell from the air inlet 115 of the shell through the air supply channel 21 on this side, driving the blade 14 to rotate in the forward direction.

[0035] When the vane-type pneumatic motor 1 needs to work in reverse, the air control valve core 22 moves from the middle stop position toward the housing forward flow channel 111 (ie, toward Figure 5 The air control valve 2 is in the reverse position, and the air supply channel 21 of the air control valve 2 is close to the reverse flow channel 112 of the shell. The compressed air enters the reverse flow channel 112 of the shell from the air inlet 115 of the shell through the air supply channel 21 on this side, driving the blade 14 to rotate in the reverse direction.

[0036] In order to connect the intake manifold 15 and the exhaust manifold 16, Figure 7 As shown, the cylinder liner 12 is provided with a cylinder liner forward flow channel 121 and a cylinder liner reverse flow channel 122. Figure 8 、 9 As shown, the cylinder liner forward flow channel 121 and the cylinder liner reverse flow channel 122 are arranged along the axial direction of the cylinder liner 12 and pass through the cylinder liner wall of the cylinder liner 12. The cylinder liner forward flow channel 121 connects the forward air inlet 151 of the intake distribution plate 15 and the forward air exhaust port 161 of the exhaust distribution plate 16, and the cylinder liner reverse flow channel 122 connects the reverse air inlet 152 of the intake distribution plate 15 and the reverse air exhaust port 162 of the exhaust distribution plate 16.

[0037] In the forward rotation mode, the air control valve 2 guides the compressed air into the housing forward rotation channel 111 through the air supply channel 21, and the compressed air enters the working cavity of the cylinder sleeve 12 through the forward rotation inlet 151 of the air distribution disc 15 and the cylinder sleeve forward rotation channel 121, drives the blade 14 to rotate forward, and is then discharged through the forward rotation outlet 161 of the exhaust distribution disc 16, thereby driving the rotation shaft 13 to rotate forward; in the reverse rotation mode, the air control valve 2 switches the air flow path, so that the compressed air enters the cylinder sleeve 12 through the housing reverse rotation channel 112, the reverse rotation inlet 152 of the air distribution disc 15 and the cylinder sleeve reverse rotation channel 122, drives the blade 14 to rotate reversely, and is then discharged through the reverse rotation outlet 162 of the exhaust distribution disc 16, thereby realizing the reverse rotation of the rotation shaft 13.

[0038] As shown in Figure 8 , 9 , in order to enable the compressed air to enter the cylinder sleeve 12, the cylinder sleeve forward rotation channel 121 and the cylinder sleeve reverse rotation channel 122 are provided with a first exhaust groove 123 in communication with the cylinder sleeve forward rotation channel 121 and the cylinder sleeve reverse rotation channel 122 at the end away from the plunger pump 3, and are provided with a second exhaust groove 124 in communication with the cylinder sleeve forward rotation channel 121 and the cylinder sleeve reverse rotation channel 122 at the end close to the plunger pump 3, and the first exhaust groove 123 and the second exhaust groove 124 are in communication with the inside of the cylinder sleeve 12, forming a channel for the compressed air to enter the working cavity. In the specific working process, after the compressed air is distributed through the forward rotation inlet 151 or the reverse rotation inlet 152 of the air distribution disc 15, part of the compressed air directly enters the inside of the cylinder sleeve 12 through the first exhaust groove 123, and part of the compressed air enters the cylinder sleeve forward rotation channel 121 or the cylinder sleeve reverse rotation channel 122 through the first exhaust groove 123, and then continues to flow and enters the inside of the cylinder sleeve 12 through the second exhaust groove 124. The compressed air entering the inside of the cylinder sleeve 12 acts on the cavity between the adjacent blades 14, thereby effectively driving the blade 14 to rotate.

[0039] As shown in Figure 7 , according to the preferred embodiment of the present application, the cylinder sleeve 12 is designed in an eccentric structure, and the inner hole axis is arranged eccentrically with the rotation axis of the rotation shaft 13, forming an eccentric distance. A plurality of rotation shaft grooves 131 are uniformly arranged on the rotation shaft 13 in the circumferential direction, and each blade 14 is slidably installed in the corresponding rotation shaft groove 131. The eccentric structure enables the blade 14 to produce radial displacement during rotation and form a periodically changing closed working cavity with the inner wall of the cylinder sleeve 12.

[0040] Further, as shown in Figure 3 , the air distribution disc 15 is provided with two groups of first blade radial thrust flow channels 153 in communication with the forward rotation inlet 151 and the reverse rotation inlet 152, respectively; as shown in Figure 4As shown, two sets of second vane radial thrust flow channels 163 are correspondingly arranged on the exhaust flow distribution disc 16, and are respectively communicated with the forward rotation exhaust port 161 and the reverse rotation exhaust port 162. The first vane radial thrust flow channel 153 and the second vane radial thrust flow channel 163 are both designed in a circular arc shape, and are communicated with the shaft groove 131.

[0041] In the working process, the compressed air enters the gap between the vane 14 and the shaft groove 131 through the first vane radial thrust flow channel 153 and the second vane radial thrust flow channel 163, and generates a radial thrust to press the vane 14 against the inner wall of the cylinder sleeve 12. The eccentrically arranged cylinder sleeve 12 cooperates with the vane 14 to form a working chamber with periodically changing volume, thereby realizing efficient conversion of pneumatic energy into mechanical energy. The arrangement of the radial thrust flow channel ensures good sealing between the vane 14 and the inner wall of the cylinder sleeve 12, especially in the starting and low-speed working conditions, effectively reducing gas leakage.

[0042] As shown in Figure 2 , 7 , the cylinder sleeve 12 is provided with a main exhaust port 125 communicated with the forward rotation exhaust port 161 and the reverse rotation exhaust port 162 on the exhaust flow distribution disc 16, and the pneumatic motor housing 11 is provided with a secondary exhaust port 113 communicated with the main exhaust port 125. An external silencer 114 is fixedly installed on the pneumatic motor housing 11, and the silencer 114 is connected to the secondary exhaust port 113 through a pipeline. In the working process, the compressed air that has completed work enters the silencer 114 through the main exhaust port 125 and the secondary exhaust port 113 in sequence, and is discharged after noise reduction treatment.

[0043] As shown in Figure 2 , the plunger pump housing 31 is detachably fixed to the end of the pneumatic motor housing 11 by bolts or other fasteners, forming an integral structure. In the assembly structure, a disc spring 171 is arranged between the plunger pump housing 31 and the exhaust flow distribution disc 16. The disc spring 171 generates a continuous axial compression force in a pre-compressed state, and sequentially compresses the exhaust flow distribution disc 16, the cylinder sleeve 12 and the intake flow distribution disc 15 against the inner end face of the pneumatic motor housing 11, so that the exhaust flow distribution disc 16, the cylinder sleeve 12 and the intake flow distribution disc 15 are kept in close contact. Figures 2-5 , 7, the exhaust flow distribution disc 16, the cylinder sleeve 12, the intake flow distribution disc 15 and the pneumatic motor housing 11 are correspondingly provided with coaxial positioning pin holes in the axial direction. As shown in Figure 2 , the positioning pin 172 sequentially penetrates the positioning pin holes of the exhaust flow distribution disc 16, the cylinder sleeve 12, the intake flow distribution disc 15 and the pneumatic motor housing 11, realizing the circumferential positioning and angular alignment between the components.

[0044] As shown in Figure 2 , 6As shown, the plunger adopts a double spring pre-tightening structure design, the plunger 33 is a spherical end away from the plunger pre-tightening spring 351, the spherical end is movably connected with the sliding shoe 352 through a ball hinge connection, so that the sliding shoe 352 can be self-adaptively in sliding contact with the inclined surface of the swash plate 34; the non-working side of the sliding shoe 352 is fixedly connected with the return disc 353, the return disc 353 cooperates with the return disc positioning sleeve 354 sleeved on the rotating shaft 13; the return disc positioning sleeve 354 and the plunger sleeve 32 are provided with the return disc compression spring 355, the spring generates a continuous axial compression force, so that the return disc positioning sleeve 354 can compress the return disc 353 and the sliding shoe 352 on the swash plate 34.

[0045] The working mechanism of the above structure is as follows: the plunger pre-tightening spring 351 acts on the plunger 33 to provide an initial radial compression force; at the same time, the return disc compression spring 355 compresses the return disc 353 and the sliding shoe 352 to the direction of the swash plate 34 through the return disc positioning sleeve 354. The two sets of spring systems work together to ensure that the sliding shoe 352 and the swash plate 34 always maintain reliable contact under various working conditions. The ball hinge connection structure allows the sliding shoe 352 to adapt to the change of the inclination angle of the swash plate 34; the double spring system provides redundant compression protection to prevent the sliding shoe 352 from being separated; the guiding effect of the return disc 353 improves the motion stability.

[0046] The new portable air-driven hydraulic pump for emergency rescue of the embodiment is used for an open hydraulic system, and the specific working process is as follows: compressed air enters the system through the air supply channel 21 of the air control valve 2, the valve core 22 of the air control valve can be switched between the forward rotation position, the reverse rotation position and the middle stop position. When in the forward rotation position, the compressed air enters the working cavity of the cylinder sleeve 12 in turn through the shell forward flow channel 111, the forward inlet port 151 of the air inlet flow distribution disc 15 and the cylinder sleeve forward flow channel 121; when in the reverse rotation position, the compressed air enters through the shell reverse flow channel 112, the reverse inlet port 152 of the air inlet flow distribution disc 15 and the cylinder sleeve reverse flow channel 122. The compressed air enters between the adjacent blades 14 through the first exhaust groove 123 and the second exhaust groove 124, pushes the blades 14 to rotate in the eccentric cylinder sleeve 12, and at the same time pushes the blades 14 to the inner wall of the cylinder sleeve through the first blade radial thrust flow channel 153 and the second blade radial thrust flow channel 163 to ensure sealing. The blades 14 drive the rotating shaft 13 to rotate, and the plunger sleeve 32 is driven to rotate under the support of the needle bearing 321 through the key connection. The plunger 33 is always in contact with the swash plate 34 through the ball hinge connected sliding shoe 352 under the double action of the plunger pre-tightening spring 351 and the return disc compression spring 355. When the plunger sleeve 32 rotates, a plurality of plungers 33 make reciprocating motion with phase difference under the action of the inclined surface of the swash plate 34: when the plunger 33 moves towards the swash plate 34, the pump cavity volume increases to suck oil from the oil tank; when moving away from the swash plate 34, the oil liquid is compressed to form high pressure output, realizing continuous and stable hydraulic oil supply to drive the hydraulic cylinder and other actuators to work. The compressed air completing work is discharged through the exhaust flow distribution disc 16, the main exhaust port 125 of the cylinder sleeve 12, the auxiliary exhaust port 113 of the air motor shell 11 and the silencer 114. The air-driven hydraulic pump directly drives the plunger pump 3 through the vane type air motor 1, discards the traditional air cylinder reciprocating mechanism, has the advantages of small size, light weight, low vibration and noise, and is especially suitable for use in explosion-proof fields such as coal mines and chemical industry and underwater emergency rescue.

[0047] Specific embodiment two: the new portable air-driven hydraulic pump for emergency rescue of specific embodiment one is used for an open hydraulic system, and the hydraulic station needs to be configured with a large volume oil tank, and the overall weight of the rescue equipment is relatively heavy. In order to overcome this defect and further improve the portability of the equipment, an improved scheme suitable for semi-closed and closed hydraulic systems is proposed in the embodiment.

[0048] The semi-closed and closed hydraulic system can significantly reduce the volume of the oil tank through the internal oil circulation design (the closed hydraulic system only uses a small oil tank to meet the use requirements), thereby further effectively reducing the overall weight of the rescue equipment. However, when the semi-closed and closed system drives the hydraulic cylinder to work, the effective area difference between the rod cavity and the rodless cavity will cause the oil volume imbalance, which is specifically manifested as follows: when the hydraulic cylinder reciprocates, the oil volume required by the rodless cavity is greater than the oil volume discharged from the rod cavity. This imbalance will cause the system pressure to fluctuate and the actuator to move unstably. To solve this technical problem, the embodiment integrates the plunger pump flow distribution block 4 and the oil supplementing balance valve 5 on the basis of the air-driven hydraulic pump in the first embodiment, uses the plunger pump flow distribution block 4 and the oil supplementing balance valve 5 to automatically compensate for the oil volume difference caused by the area difference, and maintains the system pressure stable. The design scheme realizes the stable operation of the semi-closed and closed system through the following specific technical means: As shown in Figure 10 , the plunger pump flow distribution block 4 is fixedly installed on the plunger pump shell 31, and the oil supplementing balance valve 5 is integrated in the plunger pump flow distribution block 4. As shown in Figure 11 , 12 , the first flow distribution block oil channel 41 and the second flow distribution block oil channel 42 are symmetrically arranged in the plunger pump flow distribution block 4, the flow channel of the first flow distribution block oil channel 41 and the second flow distribution block oil channel 42 is perpendicular to the axial direction of the plunger pump 3, the middle part of the first flow distribution block oil channel 41 and the second flow distribution block oil channel 42 is respectively provided with the first hydraulic oil inlet and outlet hole 411 and the second hydraulic oil inlet and outlet hole 421, and the side of the plunger pump flow distribution block 4 close to the plunger pump 3 is provided with the first flow distribution channel 431 and the second flow distribution channel 432 (shown in Figure 13 ) communicating with the pump cavity of the plunger pump 3. The first hydraulic oil inlet and outlet hole 411 communicates with the pump cavity of the plunger pump 3 through the first flow distribution channel 431, the second hydraulic oil inlet and outlet hole 421 communicates with the pump cavity of the plunger pump 3 through the second flow distribution channel 432, the first hydraulic oil inlet and outlet hole 411 can communicate with the rodless cavity of the hydraulic cylinder (not shown in the drawing), and the second hydraulic oil inlet and outlet hole 421 can communicate with the rod cavity of the hydraulic cylinder (not shown in the drawing).

[0049] As shown in Figure 11 , 12 , the oil return and supplement channel 44 is perpendicular to the first flow distribution block oil channel 41 and the second flow distribution block oil channel 42, and the oil return and supplement channel 44 is perpendicular to the axial direction of the plunger pump 3. The oil supplementing balance valve 5 is installed in the oil return and supplement channel 44, and the oil return and supplement channel 44 is provided with the oil return and supplement port 441 (shown in Figure 10The oil return and supplement port 441 can be connected with an oil tank (or an oil bag), and the plunger pump housing 31 is provided with a plunger pump oil suction channel 311 connected with the plunger pump cavity and the oil return and supplement channel 44. In the embodiment, the oil return and supplement port 441 is communicated with the oil tank (or the oil bag) through the filter element 45, so that the hydraulic oil in the oil tank (or the oil bag) can enter the plunger pump cavity of the plunger pump 3 through the oil return and supplement channel 44 and the plunger pump oil suction channel 311 after being filtered.

[0050] As shown in Figure 11 , 12 The oil return and supplement port 441 can be connected with an oil tank (or an oil bag), and the plunger pump housing 31 is provided with a plunger pump oil suction channel 311 connected with the plunger pump cavity and the oil return and supplement channel 44. In the embodiment, the oil return and supplement port 441 is communicated with the oil tank (or the oil bag) through the filter element 45, so that the hydraulic oil in the oil tank (or the oil bag) can enter the plunger pump cavity of the plunger pump 3 through the oil return and supplement channel 44 and the plunger pump oil suction channel 311 after being filtered. Figure 11 , 12 The shape of the spool valve spool 51 is dumbbell-shaped, and the first valve block 512 and the second valve block 513 form an oil return and supplement valve oil port 514 communicated with the oil return and supplement port 441. The side opening of the oil return and supplement channel 44 is closed by the plug 52, the first reset spring 531 is arranged between the first valve block 512 and the oil return and supplement channel 44, and the second reset spring 532 is arranged between the second valve block 513 and the plug 52. The first reset spring 531 and the second reset spring 532 can make the spool valve spool 51 in the middle position in the initial state, that is, the spool valve spool 51 is located in the middle part of the oil return and supplement channel 44. Figure 11 The spool valve spool 51 is in the middle position.

[0051] In the embodiment, when the rotating shaft 13 drives the plunger sleeve 32 to rotate in the positive direction, the hydraulic pump establishes a positive oil circuit, and the hydraulic oil in the plunger pump cavity of the plunger pump 3 is output to the rodless cavity of the hydraulic cylinder through the first hydraulic oil inlet and outlet hole 411 after being distributed by the first distribution channel 431, so that the hydraulic cylinder is extended. At this time, the rod cavity (communicated with the second hydraulic oil inlet and outlet hole 421) of the hydraulic cylinder needs to discharge less oil due to the area difference. In order to make the rod cavity discharge oil, the hydraulic oil output through the first hydraulic oil inlet and outlet hole 411 also flows into the oil return and supplement channel 44 on the side close to the first distribution block oil channel 41 (that is, the left side in Figure 11 At this time, the pressure on the first distribution block oil channel 41 side in the oil return and supplement channel 44 is greater than the pressure on the second distribution block oil channel 42 side (that is, the pressure on the left side in Figure 11 The spool valve spool 51 of the oil return and supplement valve 5 moves towards the second distribution block oil channel 42 under the oil pressure of the hydraulic oil (that is, towards Figure 11When the rotating shaft 13 drives the plunger sleeve 32 to rotate reversely, the hydraulic pump establishes a reverse oil path, and the hydraulic oil in the plunger pump 3 is output to the hydraulic cylinder rod cavity through the second hydraulic oil inlet and outlet hole 421 after being distributed by the second distribution block oil channel 42, and the hydraulic cylinder retracts. At this time, the rodless cavity of the hydraulic cylinder (communicates with the first hydraulic oil inlet and outlet hole 411) needs to supplement more oil due to the area difference. In order to supplement the oil into the rodless cavity, the hydraulic oil output through the second hydraulic oil inlet and outlet hole 421 also flows into the oil return and oil supplement channel 44 on the side close to the second distribution block oil channel 42 (that is, the right side in

[0052] When the rotating shaft 13 drives the plunger sleeve 32 to rotate reversely, the hydraulic pump establishes a reverse oil path, and the hydraulic oil in the plunger pump 3 is output to the hydraulic cylinder rod cavity through the second hydraulic oil inlet and outlet hole 421 after being distributed by the second distribution block oil channel 42, and the hydraulic cylinder retracts. At this time, the rodless cavity of the hydraulic cylinder (communicates with the first hydraulic oil inlet and outlet hole 411) needs to supplement more oil due to the area difference. In order to supplement the oil into the rodless cavity, the hydraulic oil output through the second hydraulic oil inlet and outlet hole 421 also flows into the oil return and oil supplement channel 44 on the side close to the second distribution block oil channel 42 (that is, the right side in Figure 11 Figure 11 When the rotating shaft 13 drives the plunger sleeve 32 to rotate reversely, the hydraulic pump establishes a reverse oil path, and the hydraulic oil in the plunger pump 3 is output to the hydraulic cylinder rod cavity through the second hydraulic oil inlet and outlet hole 421 after being distributed by the second distribution block oil channel 42, and the hydraulic cylinder retracts. At this time, the rodless cavity of the hydraulic cylinder (communicates with the first hydraulic oil inlet and outlet hole 411) needs to supplement more oil due to the area difference. In order to supplement the oil into the rodless cavity, the hydraulic oil output through the second hydraulic oil inlet and outlet hole 421 also flows into the oil return and oil supplement channel 44 on the side close to the second distribution block oil channel 42 (that is, the right side in Figure 14

[0053] In summary, the present embodiment effectively solves the problem of oil imbalance in semi-closed and closed hydraulic systems caused by the area difference between the rod cavity and the rodless cavity of the hydraulic cylinder by integrating the plunger pump distribution block 4 and the oil supplement balance valve 5 on the plunger pump 3. The first distribution block oil channel 41 and the second distribution block oil channel 42 are arranged in the distribution block to form a complete oil path control system. When the hydraulic cylinder is working, the pressure difference drives the spool valve core 51 of the oil supplement balance valve 5 to move, and the oil path communication state is automatically adjusted: during forward rotation, high-pressure oil pushes the spool valve core 51 to make the excess oil in the rod cavity return to the oil tank (or oil bag) through the oil return and oil supplement port 441; during reverse rotation, the spool valve core 51 moves reversely to make the oil in the oil tank (or oil bag) supplement into the rodless cavity. This self-adaptive oil path adjustment mechanism not only ensures the stability of the hydraulic cylinder action, but also maintains the balance of the system oil amount. The oil supplement balance valve 5 is integrated in the plunger pump distribution block 4, and the plunger pump distribution block 4 integrates the distribution and oil supplement functions, optimizes the system layout, and further reduces the equipment volume through integrated design. This design takes into account the lightweight advantage and oil balance demand of semi-closed and closed systems, and provides an efficient and reliable hydraulic power solution for emergency rescue equipment. ​​

[0054] The remaining technical features and specific embodiments of the new portable air-driven hydraulic pump for emergency rescue of the present embodiment are the same.

[0055] Figure 15 The structure diagram of the new portable air-driven hydraulic pump for emergency rescue of the present embodiment applied to a semi-closed hydraulic system. The air-driven hydraulic pump is connected with the oil tank 600, low-pressure hydraulic oil is sucked from the oil tank 600, after the pressurization of the air-driven hydraulic pump, high-pressure oil is output from the plunger pump 3 to the working cavity of the hydraulic cylinder 710 to drive the emergency rescue tool 720 to act, at the same time, the oil balance valve 5 automatically adjusts the oil amount according to the area difference between the rod cavity and the rodless cavity, and when it is insufficient, it is supplemented from the oil tank 600, and when it is excessive, it is returned to the oil tank 600.

[0056] ​ The structure diagram of the new portable air-driven hydraulic pump for emergency rescue of the present embodiment applied to a closed hydraulic system. The air-driven hydraulic pump is connected with the oil tank 600, low-pressure hydraulic oil is sucked from the oil tank 600, after the pressurization of the air-driven hydraulic pump, high-pressure oil is output from the plunger pump 3 to the working cavity of the hydraulic cylinder 710 to drive the emergency rescue tool 720 to act, at the same time, the oil balance valve 5 automatically adjusts the oil amount according to the area difference between the rod cavity and the rodless cavity, and when it is insufficient, it is supplemented from the oil tank 600, and when it is excessive, it is returned to the oil tank 600.

[0057] The above is only a specific embodiment of the present application, but the protection scope of the present application is not limited thereto, any skilled person in the art can easily think of changes or replacements within the technical range disclosed by the present application, which should be covered within the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. A new type of portable air-driven hydraulic pump for emergency rescue, characterized by: include: A vane-type pneumatic motor (1) comprises a pneumatic motor housing (11), a cylinder sleeve (12) being fixed in the pneumatic motor housing (11), a rotatable shaft (13) being provided in the cylinder sleeve (12), a plurality of blades (14) being mounted on the shaft (13), and an intake manifold (15) and an exhaust manifold (16) being fixed on both sides of the cylinder sleeve (12); An air control valve (2) is integrated on the air motor housing (11) and is capable of communicating with air inlets (151, 152) on the air inlet distribution plate (15), and the air inlets (151, 152) on the air inlet distribution plate (15) are communicated with exhaust ports (161, 162) on the exhaust distribution plate (16); A plunger pump (3) comprises a plunger pump housing (31), a plunger sleeve (32) disposed in the plunger pump housing (31), a plurality of plungers (33) slidably mounted in the plunger sleeve (32), and a swash plate (34) fixed in the plunger pump housing (31); a plunger preload spring (351) is provided between the plunger sleeve (32) and the plunger (33) to keep the plunger (33) in contact with the swash plate (34); and the plunger sleeve (32) is key-connected to a rotating shaft (13) of a vane-type pneumatic motor (1); The air control valve (2) controls the compressed air to enter the cylinder sleeve (12) through the air inlet (151, 152) of the air inlet distribution plate (15), thereby driving the blade (14) to rotate and then driving the rotating shaft (13) and the plunger sleeve (32) to rotate, so that the plunger (33) reciprocates under the action of the swash plate (34), thereby realizing the suction and pressurized output of hydraulic oil.

2. The novel portable air-driven hydraulic pump for emergency rescue according to claim 1 is characterized in that: The pneumatic motor housing (11) is provided with a housing forward flow channel (111) and a housing reverse flow channel (112) that are communicable with the air supply channel (21) of the air control valve (2); The air inlet distribution plate (15) is provided with a forward air inlet (151) communicating with the forward flow channel (111) of the shell and a reverse air inlet (152) communicating with the reverse flow channel (112) of the shell, and the air exhaust distribution plate (16) is provided with a forward exhaust port (161) communicating with the forward air inlet (151) and a reverse exhaust port (162) communicating with the reverse air inlet (152).

3. The novel portable air-driven hydraulic pump for emergency rescue according to claim 2 is characterized in that: The air-controlled valve (2) is a three-position air-controlled valve having a forward rotation position, a reverse rotation position, and a neutral stop position; When the air control valve (2) is in the forward rotation position, its air supply passage (21) is connected to the forward rotation flow passage (111) of the air motor housing (11), and the compressed air enters the cylinder sleeve (12) through the forward rotation flow passage (111) and the forward rotation air inlet (151) of the air intake distribution plate (15) and can be discharged through the forward rotation exhaust port (161) of the exhaust distribution plate (16), thereby driving the blades (14) and the rotating shaft (13) to rotate in the forward direction; When the air control valve (2) is in the reverse position, its air supply passage (21) communicates with the housing reverse flow passage (112) of the air motor housing (11), and compressed air enters the cylinder sleeve (12) through the housing reverse flow passage (112) and the reverse air inlet (152) of the air intake distribution plate (15) and can be discharged through the reverse exhaust port (162) of the exhaust distribution plate (16), thereby driving the blades (14) and the rotating shaft (13) to rotate in the reverse direction.

4. The novel portable air-driven hydraulic pump for emergency rescue according to claim 3 is characterized in that: A through-type cylinder liner forward flow channel (121) and a cylinder liner reverse flow channel (122) are provided in the axial direction on the cylinder liner (12); the cylinder liner forward flow channel (121) is connected to the forward air inlet (151) of the air intake distribution plate (15) and the forward air outlet (161) of the exhaust distribution plate (16); and the cylinder liner reverse flow channel (122) is connected to the reverse air inlet (152) of the air intake distribution plate (15) and the reverse air outlet (162) of the exhaust distribution plate (16); Compressed air can enter the cylinder liner (12) through the housing forward flow passage (111), the forward air inlet (151) of the air inlet distribution plate (15), and the cylinder liner forward flow passage (121), and can be discharged through the forward exhaust port (161) of the exhaust distribution plate (16), thereby driving the blades (14) and the rotating shaft (13) to rotate in the forward direction; The compressed air can enter the cylinder liner (12) through the shell reversing flow channel (112), the reversing air inlet (152) of the air inlet distribution plate (15), and the cylinder liner reversing flow channel (122), and can be discharged through the reversing exhaust port (162) of the exhaust distribution plate (16), thereby driving the blades (14) and the rotating shaft (13) to rotate in the opposite direction.

5. The novel portable air-driven hydraulic pump for emergency rescue according to claim 4 is characterized in that: Exhaust grooves (123, 124) connected to the cylinder liner forward flow channel (121) and the cylinder liner reverse flow channel (122) are provided at both ends of the cylinder liner forward flow channel (121) and the cylinder liner reverse flow channel (122). The exhaust grooves (123, 124) are connected to the interior of the cylinder liner (12). Compressed air can enter the cavity between adjacent blades (14) in the cylinder liner (12) through the exhaust grooves (123, 124) to drive the blades (14) to rotate.

6. The novel portable air-driven hydraulic pump for emergency rescue according to claim 2 is characterized in that: The cylinder sleeve (12) is an eccentric cylinder sleeve, the inner hole of which is not concentric with the rotating shaft (13), the rotating shaft (13) is provided with a plurality of rotating shaft grooves (131), and the blades (14) are slidably mounted in the rotating shaft grooves (131); The intake distribution plate (15) is provided with a first blade radial thrust flow channel (153) communicating with the forward rotation intake port (151) or the reverse rotation intake port (152), and the exhaust distribution plate (16) is provided with a second blade radial thrust flow channel (163) communicating with the forward rotation exhaust port (161) or the reverse rotation exhaust port (162). Compressed air can enter the gap between the blade (14) and the shaft groove (131) through the first blade radial thrust flow channel (153) and the second blade radial thrust flow channel (163), so as to push the blade (14) toward the inner wall of the cylinder sleeve (12).

7. The novel portable air-driven hydraulic pump for emergency rescue according to claim 2 is characterized in that: The cylinder sleeve (12) is provided with a main exhaust port (125) which is in communication with the forward exhaust port (161) and the reverse exhaust port (162) on the exhaust distribution plate (16); the pneumatic motor housing (11) is provided with a secondary exhaust port (113) which is in communication with the main exhaust port (125); a muffler (114) connected to the secondary exhaust port (113) is fixed to the pneumatic motor housing (11); compressed air passes through the main exhaust port (125) and the secondary exhaust port (113) and is discharged through the muffler (114).

8. The novel portable air-driven hydraulic pump for emergency rescue according to claim 1 is characterized in that: The end of the plunger (33) away from the plunger preload spring (351) is a spherical end, and the spherical end is hinged with a sliding shoe (352) that can slide in contact with the slant plate (34). A return plate (353) is fixed on the side of the sliding shoe (352) that is not in contact with the slant plate (34). A return plate positioning sleeve (354) is sleeved on the rotating shaft (13). A return plate pressing spring (355) is provided between the return plate positioning sleeve (354) and the plunger sleeve (32). Under the elastic force of the return plate pressing spring (355), the return plate positioning sleeve (354) can press the return plate (353) and the sliding shoe (352) onto the slant plate (34).

9. The novel portable air-driven hydraulic pump for emergency rescue according to claim 1 is characterized in that: A plunger pump flow distribution block (4) is fixedly mounted on the plunger pump housing (31), and an oil replenishment balancing valve (5) is integrated in the plunger pump flow distribution block (4); The plunger pump distribution block (4) is provided with a first distribution block oil passage (41) and a second distribution block oil passage (42). The first distribution block oil passage (41) and the second distribution block oil passage (42) are provided with a first hydraulic oil inlet and outlet hole (411) and a second hydraulic oil inlet and outlet hole (421) respectively. The first hydraulic oil inlet and outlet hole (411) and the second hydraulic oil inlet and outlet hole (421) are communicated with the pump chamber of the plunger pump (3) through a first distribution channel (431) and a second distribution channel (432) respectively provided on the plunger pump distribution block (4). The oil inlet and outlet holes (411) and the second hydraulic oil inlet and outlet holes (421) can be communicated with the rodless chamber of the hydraulic cylinder and the rod chamber of the hydraulic cylinder respectively. A return oil replenishment channel (44) communicating with the first distribution block oil passage (41) and the second distribution block oil passage (42) is provided in the plunger pump distribution block (4). The replenishment balance valve (5) is installed in the return oil replenishment channel (44). The return oil replenishment channel (44) is provided with a return oil replenishment port (441) communicating with the return oil replenishment channel (44). The return oil replenishment port (441) can be communicated with an oil tank or an oil bag.

10. The novel portable air-driven hydraulic pump for emergency rescue according to claim 9 is characterized in that: The oil replenishment balancing valve (5) includes a sliding valve core (51) slidably mounted in the oil return replenishment channel (44), the sliding valve core (51) includes a valve stem (511) and a first valve block (512) and a second valve block (513) fixedly mounted on the valve stem (511) and arranged at a certain distance, an oil replenishment balancing valve oil port (514) communicating with the oil return replenishment port (431) is formed between the first valve block (512) and the second valve block (513), the opening of the oil return replenishment channel (44) is closed by a screw plug (52), a first return spring (531) is provided between the first valve block (512) and the oil return replenishment channel (43), and a second return spring (532) is provided between the second valve block (513) and the screw plug (52); When the pressure on the side of the first distribution block oil passage (41) is greater than the pressure on the side of the second distribution block oil passage (42), the spool valve (51) moves toward the second distribution block oil passage (42), so that the oil replenishment balance valve oil port (514) is communicated with the second distribution block oil passage (42); when the pressure on the side of the second distribution block oil passage (42) is greater than the pressure on the side of the first distribution block oil passage (41), the spool valve (51) moves toward the first distribution block oil passage (41), so that the oil replenishment balance valve oil port (514) is communicated with the first distribution block oil passage (41).

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