Double piston supercharged cylinder with cooling structure

Abstract

The application discloses a double-piston pressurizing cylinder with a cooling structure, which comprises a cylinder barrel, one end of which is provided with a cylinder end cover, the other end of the cylinder barrel is provided with an oil cylinder end cover, and a piston rod is located in the cylinder barrel through the oil cylinder end cover; a piston comprises a main piston and a secondary piston, the main piston is movably arranged in the cylinder barrel, the secondary piston is arranged in the cylinder barrel and closely arranged on the main piston, and the piston rod is connected with the secondary piston; and an end cover is provided with a cooling structure. The application avoids the emergence of partial load by adding a guide secondary piston which is fixedly connected with the piston rod, so that the main piston has good centering property, partial wear is reduced, the service life of the pressurizing cylinder is prolonged, and the clearance and intake heating are reduced by the arrangement of the cooling structure, so that the volumetric efficiency is improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressor supercharging. More particularly, the present application relates to a double-piston supercharging cylinder with a cooling structure. BACKGROUND

[0002] Hydrogen energy is a secondary energy source with wide sources, clean and carbon-free, flexible and efficient, and rich application scenarios. Hydrogen refueling station is a gas station that stores hydrogen gas of different sources in high-pressure tanks in the station through a compressor, and then fills hydrogen gas for hydrogen fuel cell vehicles through a hydrogen dispenser. As a core hub connecting the upstream and downstream industry chains, the hydrogen refueling station has become a key link in the development of hydrogen energy industry. The compressor is one of the core equipment of the hydrogen refueling station, and the liquid-driven piston compressor has the advantages of adapting to frequent start and stop, high volumetric efficiency, simple structure, easy maintenance, etc., and is one of the main application forms of the hydrogen refueling station.

[0003] Since the gas cavity is a high-purity high-pressure hydrogen environment, if the main piston is directly connected with the piston rod, the piston rod is prone to bending deformation due to the influence of gravity and assembly error, thereby causing the piston to be eccentrically worn. Meanwhile, in a high-temperature and high-pressure environment, the sealing ring is prone to damage, and if the sealing element needs to be replaced, the entire supercharging cylinder needs to be disassembled to take out and replace the piston.

[0004] A large amount of heat is generated in the compression process of the gas, resulting in a very high temperature of the cylinder barrel and the cylinder head. The temperature rise is particularly obvious at the exhaust end zone, i.e., the cylinder head. The high temperature of the cylinder head heats the intake passage. For a high-pressure compressor, a large amount of compression heat is generated, and the intake heating phenomenon is more obvious, which significantly reduces the temperature coefficient, thereby reducing the efficiency of the compressor. The existing supercharging cylinder structure mostly only cools the cylinder barrel, without considering the cooling of the cylinder head. SUMMARY

[0005] An object of the present application is to provide a double-piston supercharging cylinder with a cooling structure. A guide secondary piston is fixedly connected with the piston rod to avoid eccentric loading, so that the main piston has good centering property, and the replacement of the sealing element on the main piston is facilitated.

[0006] In order to achieve these objects and other advantages and in accordance with the purpose of the application, a double-piston supercharging cylinder with a cooling structure is provided, which comprises: a cylinder barrel, one end of which is provided with a cylinder head, and the other end of which is provided with an oil cylinder head, and a piston rod passes through the oil cylinder head and is located in the cylinder barrel; a piston comprising a main piston and a secondary piston, the main piston being movably arranged in the cylinder barrel, and the secondary piston being arranged in the cylinder barrel in close contact with the main piston, and the piston rod being connected with the secondary piston.

[0007] Preferably, the main piston is provided with a check ring, a sealing ring and a guide ring, the guide ring is recessed on the outer periphery of the main piston, the sealing ring is also recessed on the outer periphery of the main piston, and the check ring is also recessed on the outer periphery of the main piston and close to the end face of the main piston on the side of the cylinder head cover, the check ring completely covers the end face of the main piston to form an annulus with a gap of less than 1mm between the end face of the main piston and the inner wall of the cylinder barrel; the secondary piston is provided with a guide ring recessed on the outer periphery of the secondary piston; the center of the main piston towards the cylinder head cover is provided with a tool hole.

[0008] Preferably, the cylinder head cover is provided with an air inlet valve and an air outlet valve through the valve cover, the air inlet valve is connected to the air chamber in the cylinder barrel through the air inlet channel provided in the cylinder head cover, and the air outlet valve is also connected to the air chamber in the cylinder barrel through the air outlet channel provided in the cylinder head cover.

[0009] Preferably, the air inlet channel and the air outlet channel are inclined linearly towards the central axis of the cylinder barrel, forming an eight-shaped structure.

[0010] Preferably, the oil cylinder end cover is connected with an oil cylinder barrel at the rear, the piston rod is connected with the oil cylinder piston in the oil cylinder barrel and is driven by hydraulic oil pressure, the oil cylinder end cover is respectively connected with an oil inlet and return port and a drain port, and the two sides of the oil cylinder barrel are symmetrically provided with two double-piston cylinders, and the two ends of the piston rod are respectively connected with the secondary pistons in the cylinder barrels on the two sides.

[0011] Preferably, the air chamber in the cylinder barrel and the oil chamber in the oil cylinder barrel are provided with an isolation chamber in the middle, which is located in the cylinder barrel, the isolation chamber is connected with two connection ports, which are A port and B port respectively, the A port is connected to nitrogen with a pressure of 0.1-0.2MPa, and the B port is connected to an oil collecting box, which is provided with a liquid level display.

[0012] Preferably, the front end of the piston rod connected with the secondary piston is provided with a variable cross-section, and a proximity switch is provided on the isolation chamber, which is used to detect the movement position of the piston by detecting the change of the cross-sectional area of the piston rod.

[0013] Preferably, a flow meter is provided on the isolation chamber for monitoring the leakage of gas.

[0014] Preferably, the outer periphery of the cylinder barrel on both sides is provided with a cooling water jacket, and the cylinder head cover on both sides is provided with a water inlet channel in the center, the cylinder head cover is provided with a plurality of water outlet channels around the outer periphery of the water inlet channel, one end of the plurality of water outlet channels close to the inside of the cylinder barrel is connected to the water inlet channel to form an umbrella-shaped structure, and the other end of the plurality of water outlet channels away from the inside of the cylinder barrel is connected to the water outlet chamber.

[0015] Preferably, the cooling water inlet is communicated to one side of the cooling water jacket, then flows out from the other side of the cooling water jacket, then flows into the cylinder head cover through the water inlet channel, and finally flows out into the water outlet cavity through the water outlet channel and is communicated to the cooling water outlet; or one of the cooling water inlets is communicated to one side of the cooling water jacket, then flows out from the other side of the cooling water jacket and is communicated to the cooling water outlet, and the other cooling water inlet flows into the cylinder head cover through the water inlet channel, then flows out into the water outlet cavity through the water outlet channel and is communicated to the cooling water outlet.

[0016] The present application at least includes the following beneficial effects:

[0017] 1、The present application sets double pistons, sets the main piston as a free state, and has no connection with other components, and increases a guide vice piston which is fixedly connected with the piston rod, so that the phenomenon of partial load is avoided, the main piston has good centering, the service life of the sealing element is improved, the service time of the supercharged cylinder is improved, and the maintenance frequency is reduced.

[0018] 2、The present application also sets a cooling structure at the cylinder head cover, cools the cylinder head cover, increases the heat exchange area, improves the cooling effect, so that the high-temperature heating of the intake passage of the cylinder head cover is avoided as much as possible, the intake passage approaches constant temperature, the volumetric efficiency is improved, and the compressor efficiency is improved.

[0019] 3、The present application sets double pistons, and since the main piston is in a free state, when the sealing element on the main piston needs to be replaced, only the cylinder head cover needs to be disassembled, and the main piston is taken out through the tool hole, so that the sealing element can be replaced, and the entire supercharged cylinder does not need to be disassembled.

[0020] 4、The blocking ring of the present application adopts a customized blocking ring structure, and only a small annular space exists between the main piston and the cylinder barrel wall after installation, the residual volume is reduced, and the working efficiency is improved.

[0021] 5、The intake passage and the exhaust passage of the present application are set as a mutton-tail shape structure, so that the relative residual volume of the entire structure is smaller, and the efficiency is higher.

[0022] Other advantages, objects, and features of the present application will be partly embodied by the following description, and will be partly understood by those skilled in the art through research and practice of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0023] Figure 1 It is a structure schematic diagram of the supercharged cylinder of the present application;

[0024] Figure 2 It is a partial enlarged view of the main piston and the vice piston of the double piston of the present application;

[0025] Figure 3 It is a schematic diagram of the intake passage and the exhaust passage in the prior art which are double L-shaped channels.

[0026] Figure 4 is a partial enlarged view of the cylinder end cover of the present application;

[0027] Figure 5 is a partial enlarged view of the isolation chamber of the present application;

[0028] Figure 6 is a schematic diagram of the cooling structure in series of the present application;

[0029] Figure 7 is an axonometric view of the cylinder end cover of the present application;

[0030] Figure 8 is a schematic diagram of the connection between the retaining ring and the main piston of the present application.

[0031] Explanation of reference signs:

[0032] 1, cylinder end cover, 2, valve gland, 3, intake valve, 4, flange, 5, cooling water jacket, 6, cylinder barrel, 7, proximity switch, 8, exhaust valve, 9, main piston, 10, auxiliary piston, 11, piston rod, 12, intake passage, 13, exhaust passage, 14, oil cylinder barrel, 15, retaining ring, 16, sealing ring, 17, guide ring, 18, tooling hole, 19, oil cylinder end cover, 20, oil cylinder piston, 21, isolation chamber, 22, flowmeter, 23, water inlet passage, 24, water outlet passage, 25, water outlet cavity. DETAILED DESCRIPTION

[0033] The present application will be further described in conjunction with the accompanying drawings, so that those skilled in the art can implement it according to the description in the specification.

[0034] It should be noted that the experimental methods described in the following embodiments are conventional methods unless otherwise specified, and the reagents and materials can be obtained from commercial channels unless otherwise specified; in the description of the present application, the terms "lateral", "longitudinal", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like indicate the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application.

[0035] As Figures 1 to 8As shown, the application provides a double-piston pressurizing cylinder with cooling structure, comprising: a cylinder barrel 6, one end of which is provided with a cylinder end cover 1, the other end of the cylinder barrel 6 is provided with an oil cylinder end cover 19, and a piston rod 11 passes through the oil cylinder end cover 19 and is located in the cylinder barrel 6; a piston, comprising a main piston 9 and a secondary piston 10, the main piston 9 is movably arranged in the cylinder barrel 6, the secondary piston 10 is also arranged in the cylinder barrel 6 and closely contacts the main piston 9, and the piston rod 11 is connected to the secondary piston 10.

[0036] In the above technical solution, the main piston 9 is in a free state and is not connected with other components, and the main piston 9 reciprocates under the action of right oil pressure and left gas pressure. The piston has a large area compared with the piston rod, and in the case of no connection, misalignment is prone to occur; at the same time, the left end of the piston rod is not supported, and is similar to a cantilever beam structure, and is affected by gravity and assembly errors, deflection is generated at the end of the piston rod, and a radial component force is generated on the main piston. Therefore, the piston is prone to eccentric wear, the guide ring is prone to rapid wear, and the main piston seal and the cylinder barrel are worn.

[0037] Therefore, a guide secondary piston 10 with an outer diameter equal to that of the main piston is added and fixedly connected with the piston rod. Since the guide secondary piston does not contact hydrogen, only a guide ring 17 is installed, and the length is 1 / 3-1 / 2 of the length of the main piston; on the one hand, the contact area with the main piston is increased to avoid eccentric load in the process of movement, so that the main piston has good centration; on the other hand, the guide ring 17 on the secondary piston limits the radial displacement of the free end of the piston rod, so that the piston movement has good centration. Since the guide secondary piston does not contact hydrogen, in order to reduce the influence of the gravity of the secondary piston, a light material such as aluminum alloy can be selected. In addition, in order to avoid the wear of the guide secondary piston on the cylinder barrel after the wear of the guide ring 17, the hardness of the material of the guide secondary piston can be selected to be less than the hardness of the material of the cylinder barrel.

[0038] In addition, since the main piston 9 is in a free state, when the seal on the main piston 9 needs to be replaced, the cylinder end cover 1 is only needed to be disassembled, the main piston 9 is taken out through the tool hole 18, and the seal can be replaced without disassembling the entire pressurizing cylinder. The cylinder end cover 1 and the cylinder barrel 6 are connected through a flange 4, and the cylinder barrel 6 and the oil cylinder end cover 19 are also connected through the flange 4.

[0039] In another technical solution, as shown in FIG. 2, Figure 2 and Figure 8As shown, the main piston 9 is provided with a check ring 15, a sealing ring 16 and a guide ring 17, the guide ring 17 is recessed on the outer periphery of the main piston 9, the sealing ring 16 is also recessed on the outer periphery of the main piston 9, and the check ring 15 is also recessed on the outer periphery of the main piston 9 and close to the end face of the main piston 9 on the side of the cylinder head 1, the check ring 15 completely covers the end face of the main piston 9 to form a small annular gap with the inner wall of the cylinder barrel 6, and the gap is less than 1mm; the secondary piston 10 is provided with a guide ring 17, which is recessed on the outer periphery of the secondary piston 10; the center of the main piston 9 on the side of the cylinder head 1 is provided with a tool hole 18.

[0040] In the above technical solution, the gas cavity is a high temperature and high pressure environment, and the main piston is a high pressure dynamic seal. In order to ensure the sealing effect, a seal such as a flooding seal is generally used. In order to facilitate the installation of the sealing ring 16, the main piston is made into a split type groove, and a check ring needs to be installed in front of the groove. If the traditional check ring structure is selected, the annular gap between the check ring and the inner wall of the cylinder barrel is large, which leads to the increase of the relative clearance volume, and the working efficiency of the supercharged cylinder is reduced. Therefore, the check ring 15 is designed as a self-made stepped structure, the end face of the main piston is completely covered to form an annular gap with the inner wall of the cylinder barrel, and the gap is less than 1mm, and the check ring is fixedly connected with the main piston by four screws, which enhances the safety and reliability. The guide rings 17 on the main piston 9 and the secondary piston 10 are generally spaced apart by two. The tool hole 18 is provided for connecting the main piston 9 with the external mechanism when replacing the sealing element, and the main piston 9 is taken out of the cylinder barrel 6.

[0041] In another technical solution, as shown in the figure, Figure 4 The cylinder head 1 is provided with an intake valve 3 and an exhaust valve 8 through a valve gland 2, the intake valve 3 communicates with the gas cavity in the cylinder barrel 6 through an intake passage 12 provided in the cylinder head 1, and the exhaust valve 8 also communicates with the gas cavity in the cylinder barrel 6 through an exhaust passage provided in the cylinder head 1.

[0042] In the above technical solution, the intake valve 3 and the exhaust valve 8 are installed in the cylinder head 1 through the valve gland 2. When the compressor starts to exhaust, the exhaust valve 8 is opened, and the pressurized gas is discharged from the exhaust passage 13; the piston moves reversely, and the high pressure gas remaining in the clearance volume expands first, until the pressure of the gas in the working chamber is lower than the pressure in the compressor intake pipe, the intake valve 3 is opened, and when the compressor starts to inhale, the gas enters the cylinder from the intake passage 12.

[0043] The volumetric efficiency η of the compressor v Directly reflects the degree of effective utilization of the working volume of the cylinder of the compressor, and is one of the important parameters representing the performance of the compressor. Among them, λ vis the volume coefficient, the larger the relative clearance volume, the smaller the volume coefficient; λ p is the pressure coefficient; λ T is the temperature coefficient, mainly depends on the influence of heat exchange on the cylinder intake capacity during the intake process, the heat source of the heated gas during the intake process mainly includes the intake cavity with high temperature and the wall surface of the intake passage, the valve passage surface, the cylinder wall surface and the piston top surface. For hydrogen and other gases with good thermal conductivity, heat exchange will be more promoted, resulting in λ T decrease. In addition, if the cylinder cooling condition is poor, especially the cooling near the intake passage, the cylinder wall and valve cavity wall surface temperature will be high, and the heat transferred to the gas will be more, which will also lead to λ T decrease; λ l is the leakage coefficient.

[0044] η v = λ v . λ p . λ T . λ l

[0045] Therefore, reducing the relative clearance volume and improving the intake heating are effective means to improve the volumetric efficiency of the compressor.

[0046] In another technical scheme, the intake passage 12 and the exhaust passage 13 are both linearly arranged towards the center axis of the cylinder barrel 6, and have an eight-shaped structure. As shown in Figure 4 , the intake passage 12 and the exhaust passage 13 of the comparative example are arranged as double L-shaped passages. The relative clearance volume of the structure of the present application is smaller, and the efficiency is higher. Figure 3

[0047] In another technical scheme, as shown in Figure 1 , the oil cylinder end cover 19 is connected with an oil cylinder barrel 14 at the rear, the piston rod 11 is connected with an oil cylinder piston 20 in the oil cylinder barrel 14 and is driven to act by hydraulic oil pressure, the oil cylinder end cover 19 is respectively connected with an oil inlet and return port and a drain port, and the oil cylinder barrel 14 is symmetrically provided with two double-piston cylinders on both sides, and the piston rod 11 is respectively connected with the secondary piston 10 in the cylinder barrel 6 on both sides.

[0048] ​In the above technical solution, the hydraulic system supplies oil from the oil inlet and outlet ports on the cylinder end cover 19 to the oil chamber inside the cylinder barrel 14. The hydraulic oil pressure causes the cylinder piston 20 inside the cylinder barrel 14 to move to the right, driving the piston rod 11 and the auxiliary piston 11 inside the cylinder barrel 6. The intake valve 3 opens, and the air chamber of the cylinder barrel 6 begins the gas expansion process. Under the action of gas force, the floating main piston 9 moves to the right along with the guide auxiliary piston 10. When the cylinder piston 20 moves in the opposite direction, the air chamber undergoes a gas compression process. The floating main piston 9 and the guide auxiliary piston 10 move to the left together under the push of oil pressure. Through the above process, the gas compression and expansion process is realized. At the same time, the intake valve 3 and the exhaust valve 8 open and close with the pressure change. The two double-piston booster cylinders on both sides can be configured with the same inner diameter or different inner diameters according to actual needs.

[0049] In another technical solution, such as Figure 5 As shown, an isolation chamber 21 is provided between the air chamber in the cylinder barrel 6 and the oil chamber in the oil cylinder barrel 14. The isolation chamber 21 is located inside the cylinder barrel 6 and has two connection ports, namely port A and port B. Nitrogen gas with a pressure of 0.1 to 0.2 MPa is introduced into port A, and port B is connected to an oil collection box, which is equipped with a liquid level indicator.

[0050] In the above technical solution, an isolation chamber 21 is set between the air chamber and the oil chamber. This prevents a small amount of hydraulic oil carried out during the movement of the piston rod 11 from entering the air chamber, and also avoids gas-liquid mixing caused by the failure of the air seal or oil seal. At the same time, nitrogen gas with a pressure of 0.1 to 0.2 MPa is introduced through port A of the isolation chamber 21 to maintain a slight positive pressure inside the isolation chamber 21 and prevent air from entering the isolation chamber 21 and causing hydrogen-oxygen-oil mixing. An oil collection box with a liquid level display is connected to port B of the isolation chamber 21 to monitor hydraulic oil leakage.

[0051] In another technical solution, the front end of the piston rod 11 connected to the auxiliary piston 10 is configured with a variable cross-section, and a proximity switch 7 is provided on the isolation chamber 21, which is used to detect the reversing signal of the opposite piston by detecting the change in the cross-sectional area of ​​the piston rod 11.

[0052] In the above technical solution, another interface at the upper end of the isolation chamber 21 is used to install the proximity switch 7. The front end of the piston rod 11 is machined into a variable cross-section. When the proximity switch 7 detects the change in the cross-sectional area of ​​the piston rod 11, it outputs a signal to the reversing valve. When hydraulic drive is used, it controls the hydraulic oil to switch direction. This connection control is a conventional technology and will not be described in detail here. This application is not limited to hydraulic reversing. The proximity switch 7 is installed in the low-pressure isolation chamber 21, making installation and replacement more convenient.

[0053] In another technical solution, a flow meter 22 is provided on the isolation chamber 21 to monitor gas leakage.

[0054] In another technical solution, as shown in Figure 4 and Figure 7 cooling water jacket 5 is arranged on the outer periphery of the cylinder barrel 6 on both sides, and the water inlet passage 23 is arranged in the center of the cylinder head 1 on both sides. A plurality of water outlet passages 24 are arranged on the outer periphery of the water inlet passage 23 in the cylinder head 1, and the one end of the plurality of water outlet passages 24 close to the inside of the cylinder barrel 6 is communicated with the water inlet passage 23 to form an umbrella-shaped structure, and the other end of the plurality of water outlet passages 24 away from the inside of the cylinder barrel 6 is communicated into the water outlet cavity 25.

[0055] In the above technical solution, a large amount of heat is generated during the compression of the gas, resulting in a high temperature of the cylinder barrel 6 and the cylinder head 1. The temperature rise is particularly obvious at the exhaust end zone, i.e. the cylinder head 1. The high temperature of the cylinder head 1 heats the intake passage 12, and for a high-pressure compressor, a large amount of compression heat is generated. The intake heating phenomenon is more obvious, which significantly reduces the temperature coefficient, thereby reducing the efficiency of the compressor. The existing supercharging cylinder structure mostly only cools the cylinder barrel 6 without considering the cooling of the cylinder head 1. The cooling water jacket 5 is used to cool the cylinder barrel 6, and the umbrella-shaped water inlet passage 23 and water outlet passage 24 arranged on the cylinder head 1 are used to cool the cylinder head 1. The cooling water enters the cylinder head 1 along the water inlet passage from the C port. A plurality of round holes are processed on the cylinder head 1 to form the umbrella-shaped water outlet passage 24. The water of all the water outlet passages 24 converges in the water outlet cavity 25 formed by the cylinder head 1 and the cooling cover, and finally is discharged out of the cylinder head 1 through the D port. The plurality of cooling water outlet passages 24 form an umbrella-shaped cooling structure. The heat of the cylinder head 1 is taken away by continuously flowing in and out of the cooling water, the temperature of the intake passage and the exhaust passage is reduced, the intake heating is improved, the exhaust temperature is reduced, and the volumetric efficiency of the compressor is improved.

[0056] In another technical solution, as shown in Figure 6 the cooling water inlet is communicated to one side of the cooling water jacket 5, then flows out from the other side of the cooling water jacket 5, then flows into the cylinder head through the water inlet passage 23, and finally flows out from the water outlet passage 24 into the water outlet cavity 25 and is communicated to the cooling water outlet; or one of the cooling water inlets is communicated to one side of the cooling water jacket 5, then flows out from the other side of the cooling water jacket 5 and is communicated to the cooling water outlet, and the other cooling water inlet flows into the cylinder head through the water inlet passage 23, then flows out from the water outlet passage 24 into the water outlet cavity 25 and is communicated to the cooling water outlet.

[0057] In the above technical solution, the cooling water enters the left and right cooling water jackets 5 from the inlet, and after cooling the cylinder barrel 6, the cooling water enters the left and right cylinder heads 1 to cool the cylinder heads 1, and the cooling water of the left and right cylinder heads 1 is collected and discharged from the outlet. The water path for cooling the cylinder barrel 6 and the cylinder head 1 can be connected in series as described above, which has the advantages of simple connection, low water consumption, and full use of cooling water, such as Figure 6 the connection mode shown. Alternatively, the two water paths can be connected in parallel, which has the advantages of low cooling water temperature, full cooling of the cylinder barrel 6 and the cylinder head 1, and independent adjustment of the cooling water volume.

[0058] Although the embodiments of the present application have been disclosed as above, they are not limited to the application listed in the specification and the embodiments, and can be fully applied to various fields suitable for the present application, and other modifications can be easily realized by those skilled in the art, and therefore the present application is not limited to specific details and the figures shown and described herein, without departing from the general concept defined by the claims and the equivalent scope.

Claims

1. A double-piston supercharged cylinder with cooling structure, characterized by, The utility model provides a kind of cylinder, including: Cylinder barrel, one end of which is provided with cylinder end cover, the other end of which is provided with oil cylinder end cover, and piston rod is located in the cylinder barrel through oil cylinder end cover; Piston, including main piston and auxiliary piston, the main piston is movably arranged in the cylinder barrel, and the auxiliary piston is also arranged in the cylinder barrel closely to the main piston, and the piston rod is connected to the auxiliary piston; The main piston is provided with a retaining ring, a sealing ring and a guide ring, the guide ring is recessed on the outer periphery of the main piston, the sealing ring is also recessed on the outer periphery of the main piston, and the retaining ring is also recessed on the outer periphery of the main piston and close to the end face of the main piston on the side of the cylinder end cover, the retaining ring is designed as a self-made structure with steps, which completely covers the end face of the main piston to form an annulus with a gap of less than 1mm between the end face of the main piston and the inner wall of the cylinder barrel, and the auxiliary piston is also provided with a guide ring, which is recessed on the outer periphery of the auxiliary piston, and the center of the main piston towards the cylinder end cover is provided with a tool hole.

2. The dual-piston intensifier cylinder with cooling structure of claim 1, wherein, The cylinder end cover is provided with an air inlet valve and an air outlet valve through a valve gland, the air inlet valve is connected to the air cavity in the cylinder barrel through an air inlet channel arranged in the cylinder end cover, and the air outlet valve is also connected to the air cavity in the cylinder barrel through an air outlet channel arranged in the cylinder end cover.

3. The dual-piston intensifier cylinder with cooling structure of claim 2, wherein, The air inlet channel and the air outlet channel are inclined linearly towards the central axis of the cylinder barrel, forming an eight-shaped structure.

4. The dual-piston intensifier cylinder with cooling structure of claim 1, wherein, The oil cylinder end cover is connected with an oil cylinder barrel at the back, the piston rod is connected through an oil cylinder piston in the oil cylinder barrel and driven by hydraulic oil pressure, the oil cylinder end cover is respectively connected with an oil inlet and return port and a drain port, and two double-piston cylinders are symmetrically arranged on both sides of the oil cylinder barrel.

5. The dual-piston intensifier cylinder with cooling structure of claim 4, wherein, An isolation cavity is arranged between the air cavity in the cylinder barrel and the oil cavity in the oil cylinder barrel, and the isolation cavity is connected with two connection ports, A port and B port, the A port is connected to nitrogen with a pressure of 0.1-0.2MPa, and the B port is connected to an oil collecting box, which is provided with a liquid level display.

6. The dual-piston intensifier cylinder with cooling structure of claim 5, wherein, The front end of the piston rod connected to the auxiliary piston is designed as a variable cross-section, a proximity switch is arranged on the isolation cavity, which is used to detect the change of the cross-sectional area of the piston rod to detect the reversing signal of the opposite piston.

7. The dual-piston intensifier cylinder with cooling structure of claim 5, wherein, A flowmeter is arranged on the isolation cavity.

8. The dual-piston intensifier cylinder with cooling structure of claim 4, wherein, Cooling water jackets are arranged on the outer periphery of the cylinder barrels on both sides, and water inlet channels are arranged in the centers of the cylinder end covers on both sides, a plurality of water outlet channels are arranged in a ring around the outer periphery of the water inlet channel on the cylinder end cover, one end of the plurality of water outlet channels close to the inside of the cylinder barrel is connected to the water inlet channel to form an umbrella-shaped structure, and the other end of the plurality of water outlet channels away from the inside of the cylinder barrel is connected to the water outlet cavity.

9. The dual-piston intensifier cylinder with cooling structure of claim 8, wherein, The cooling water inlet is communicated to one side of the cooling water jacket, then flows out from the other side of the cooling water jacket, then flows into the cylinder head cover through the water inlet channel, and finally flows out into the water outlet cavity through the water outlet channel and is communicated to the cooling water outlet; or one of the cooling water inlets is communicated to one side of the cooling water jacket, then flows out from the other side of the cooling water jacket and is communicated to the cooling water outlet, and the other cooling water inlet flows into the cylinder head cover through the water inlet channel, then flows out into the water outlet cavity through the water outlet channel and is communicated to the cooling water outlet.

Images