Hydraulic system for flat plate type tire vulcanizing machine

Abstract

The utility model discloses a hydraulic system for a flat plate type tire vulcanizing machine. The hydraulic system comprises a plunger cylinder V13, at least one auxiliary cylinder V12, an oil tank V1, a pump set, a lifting loop and a pressure loop, the plunger cylinder V13 and the auxiliary cylinder V12 are connected with a load through driving ends; the pump set is installed on the oil tank V1, and the auxiliary cylinder V12 is connected with the oil tank V1 and the pump set through a lifting loop. And the plunger cylinder V13 is connected with the oil tank V1 and the pump set through a pressure loop. The system has the beneficial effects that the whole set of actions of rapid rising, pressurization and pressure maintaining, pressure relief and rapid falling of the load can be achieved through one pump set, and the whole oil way structure is simple and easy to achieve.

Description

Technical Field

[0001] The present application relates to the technical field of vulcanizers, and particularly relates to a hydraulic system for a flat tire vulcanizer. Background Art

[0002] Flat vulcanizers are mainly used for the production of solid tires, and the hydraulic system of the flat vulcanizer provides power for vulcanization work. With the development of technology, the demand for solid tires is increasing. The flat vulcanizer and the demolding machine can cooperate to form multiple solid tires at one time, increasing production efficiency and meeting the production needs of solid tires. The hydraulic system is relatively simple and reliable in performance.

[0003] However, the process of manufacturing solid tires using traditional tire manufacturing methods is relatively complex and inefficient. The cost of the hydraulic system will increase significantly, and the high pressure of the hydraulic system will lead to a decrease in the service life of the corresponding valves, further increasing the maintenance cost. Moreover, current flat vulcanizers often require many pump sets to cooperate to complete an action, which also causes complexity in oil circuit control. Summary of the Utility Model

[0004] One object of the present application is to provide a hydraulic system for a flat tire vulcanizer that can solve at least one of the defects in the above background art.

[0005] To achieve at least one of the above objects, the technical solution adopted in the present application is: A hydraulic system for a flat tire vulcanizer, including a plunger cylinder V13, at least one auxiliary cylinder V12, a fuel tank V1, a pump set, a lifting circuit, and a pressure circuit; both the plunger cylinder V13 and the auxiliary cylinder V12 are connected to a load through a driving end; the pump set is installed in the fuel tank V1, and the auxiliary cylinders V12 are respectively connected to the fuel tank V1 and the pump set through the lifting circuit. The auxiliary cylinders V12 are adapted to drive the load to lift through the lifting circuit under the drive of the pump set; the plunger cylinder V13 is connected to the fuel tank V1 and the pump set through the pressure circuit; the plunger cylinder V13 is adapted to pressurize, hold pressure, and relieve pressure on the load through the pressure circuit under the drive of the pump set.

[0006] Preferably, the lifting circuit includes an electromagnetic control valve V8, a first branch, and a second branch; the first ends of the first branch and the second branch are respectively connected to the A end and the B end of the electromagnetic control valve V8, and the second ends of the first branch and the second branch are respectively connected to the rodless cavity and the rod cavity of the auxiliary cylinder V12; the P end and the T of the electromagnetic control valve V8 are respectively connected to the pump set and the fuel tank V1; the electromagnetic control valve V8 drives the auxiliary cylinder V12 to drive the load to lift by controlling the oil supply routes of the first branch and the second branch.

[0007] Preferably, the lifting circuit further includes a pilot-operated check valve V9 and a pair of one-way throttle valves V10; the pilot-operated check valve V9 is installed in the first branch, and the control end of the pilot-operated check valve V9 is connected to the second branch; the two one-way throttle valves V10 are respectively installed in the first branch and the second branch; wherein, the pilot-operated check valve V9 is close to the solenoid control valve V8.

[0008] Preferably, the lifting circuit further includes a pair of relief valves V11; the two relief valves V11 are both connected in parallel between the first branch and the second branch, and the connection directions of the two relief valves are opposite; the installation position of the relief valve V11 is on the side of the one-way throttle valve V10 close to the auxiliary cylinder V12.

[0009] Preferably, the pressure circuit includes a pilot-operated check valve V16, a solenoid control valve V17 and a solenoid ball valve V18; the pilot-operated check valve V16 is installed between the A end of the solenoid control valve V17 and the plunger cylinder V13, and the control end of the pilot-operated check valve V16 is connected to the B end of the solenoid control valve V17; the P end and the T end of the solenoid control valve V17 are respectively connected to the pump set and the fuel tank V1; the solenoid ball valve V18 is connected in parallel to the pilot-operated check valve V16 and the T end of the solenoid control valve V17.

[0010] Preferably, a filling valve V15 is connected to the oil port position of the plunger cylinder V13, and the filling valve V15 is respectively connected to the pump set and the fuel tank V1 through a control circuit and a return oil circuit; when the load is descending, the filling valve V15 is opened under the drive control of the pump set through the control circuit, and then the plunger cylinder V13 is communicated with the fuel tank V1 through the return oil circuit.

[0011] Preferably, the control circuit includes a solenoid control valve V20, the P end and the T end of the solenoid control valve V20 are respectively connected to the pump set and the fuel tank V1, and the output end of the solenoid control valve V20 is connected to the control end of the filling valve V15.

[0012] Preferably, the control circuit further includes a pressure reducing valve V21 and a one-way throttle valve V19; the P end of the solenoid control valve V20 is connected to the pump set through the pressure reducing valve V21, and the output end of the solenoid control valve V20 is connected to the control end of the filling valve V15 through the one-way throttle valve V19.

[0013] Preferably, a high-pressure ball valve V14 is further connected between the filling valve V15 and the plunger cylinder V13.

[0014] Preferably, the hydraulic system further includes an overflow valve V6 and an electromagnetic ball valve V7. The overflow valve V6 is connected between the output end of the pump unit and the fuel tank V1, and the electromagnetic ball valve V7 is connected in parallel with the overflow valve V6.

[0015] Compared with the prior art, the beneficial effects of this application are as follows:

[0016] Through a set of pump units, a complete set of actions such as the rapid rise, pressurization and pressure maintenance, pressure relief, and rapid descent of the load can be achieved, and the entire oil circuit structure is simple and easy to implement. Description of the Drawings

[0017] Figure 1 It is a schematic diagram of the overall structure of this application. Specific Embodiments

[0018] Next, in combination with specific embodiments, the present application will be further described. It should be noted that in the description of this specification, the descriptions referring to terms such as "one embodiment", "some embodiments", "example", "specific example", or "some examples" mean that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic descriptions of the above terms should not be understood as necessarily referring to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples. In addition, those skilled in the art can combine and combine the different embodiments or examples described in this specification.

[0019] In the description of the present application, it should be noted that for orientation terms, if there are terms such as "center", "transverse", "longitudinal", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc., indicating the orientation and positional relationship are based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and should not be understood as limiting the specific protection scope of the present application.

[0020] It should be noted that the terms "first", "second", etc. in the description and claims of the present application are used to distinguish similar objects and do not necessarily have to be used to describe a specific order or sequence.

[0021] In this application, unless otherwise clearly defined or limited, terms such as "installed", "connected", "linked", "fixed", etc. shall be understood in a broad sense. For example, it can be a connection, a detachable connection, or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two elements or the interaction relationship between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0022] In this application, unless otherwise clearly defined or limited, the first feature being "on" or "under" the second feature may include the direct contact between the first and second features, or may include the situation where the first and second features are not in direct contact but in contact through other features between them. Moreover, the first feature being "above", "over" and "on top of" the second feature includes that the first feature is directly above and obliquely above the second feature, or merely indicates that the horizontal height of the first feature is higher than that of the second feature. The first feature being "under", "beneath" and "underneath" the second feature includes that the first feature is directly below and obliquely below the second feature, or merely indicates that the horizontal height of the first feature is lower than that of the second feature.

[0023] The terms "comprising" and "having" in the description and claims of this application, as well as any variations thereof, are intended to cover non-exclusive inclusion. For example, a process, method, system, product or device that comprises a series of steps or units does not necessarily have to be limited to those steps or units clearly listed, but may include other steps or units not clearly listed or inherent to these processes, methods, products or devices.

[0024] One preferred embodiment of this application, such as Figure 1As shown, a hydraulic system for a flat tire vulcanizer includes a plunger cylinder V13, at least one auxiliary cylinder V12, an oil tank V1, a pump unit, a lifting circuit, and a pressure circuit. Both the plunger cylinder V13 and the auxiliary cylinder V12 are connected to the load through the driving end; among them, the auxiliary cylinder V12 is mainly used to drive the load to lift, and the plunger cylinder V13 is mainly used to pressurize and hold the pressure of the load. Specifically, the pump unit is installed in the oil tank V1, and the auxiliary cylinders V12 are all connected to the oil tank V1 and the pump unit through the lifting circuit; when the load needs to rise, the auxiliary cylinder V12 can be jacked up through the lifting circuit under the drive of the pump unit to drive the load to rise quickly and synchronously; when the load needs to fall, the auxiliary cylinder V12 can retract under the control of the lifting circuit to drive the load to fall quickly. The plunger cylinder V13 is connected to the oil tank V1 and the pump unit through the pressure circuit; when the load needs to be pressurized, the plunger cylinder V13 can be pressurized to the required design pressure through the pressure circuit under the drive of the pump unit, and then hold the pressure; when the load needs to be depressurized after completing the work, at this time, the plunger cylinder V13 can return the pressure oil to the oil tank V1 under the control of the pressure circuit to relieve the pressure.

[0025] It should be known that, compared with the traditional method of increasing the specification of the plunger pump for different load requirements, the present application realizes the high-pressure requirement of the load by combining the plunger cylinder V13 and the auxiliary cylinder V12, that is, by changing the number of the auxiliary cylinders V12 to adapt to different load requirements, and the plunger cylinder V13 is only used for pressurizing and holding the pressure after the load reaches the set position. Thus, while reducing the system cost, the speed of the load lifting is increased. At the same time, for the whole set of actions of the load's rapid rise, pressurization and pressure holding, pressure relief, and rapid fall, the present application only needs to use a set of pump units to achieve, which can further reduce the cost and simplify the entire oil circuit structure.

[0026] It can be understood that the specific number of the auxiliary cylinders V12 can be selected by those skilled in the art according to actual needs, for example Figure 1 As shown, the number of the auxiliary cylinders V12 is two. For the scenario of multiple auxiliary cylinders V12, the auxiliary cylinders V12 can be evenly arranged to ensure the stable force of the load. The specific structure and working principle of the pump unit are well known to those skilled in the art. The common pump unit structure includes a motor V2 and a plunger pump V3, and the motor V2 can drive the plunger pump V3 to transport oil.

[0027] In this embodiment, there are various specific structures of the lifting circuit. For the convenience of understanding, the following will be described in detail through one of the structures. As Figure 1As shown in the figure, the lifting circuit includes an electromagnetic control valve V8, a first branch, and a second branch. The first ends of the first branch and the second branch are respectively connected to the A end and the B end of the electromagnetic control valve V8, and the second ends of the first branch and the second branch are respectively connected to the rodless cavity and the rod cavity of the auxiliary cylinder V12; the P end and the T of the electromagnetic control valve V8 are respectively connected to the pump set and the oil tank V1; the electromagnetic control valve V8 drives the auxiliary cylinder V12 to drive the load to lift by controlling the oil supply routes of the first branch and the second branch.

[0028] Specifically, when the load needs to rise rapidly, the electromagnetic control valve V8 can connect the A end to the P end and the B end to the T end; thus, the pump set can transport the oil in the oil tank V1 from the A end of the electromagnetic control valve V8 along the first branch to the rodless cavity of the auxiliary cylinder V12, and at the same time, the oil in the rod cavity of the auxiliary cylinder V12 flows back to the oil tank V1 along the B end of the electromagnetic control valve V8 through the second branch. When the load needs to descend rapidly, the electromagnetic control valve V8 can connect the A end to the T end and the B end to the P end; thus, the pump set can transport the oil in the oil tank V1 from the B end of the electromagnetic control valve V8 along the second branch to the rod cavity of the auxiliary cylinder V12, and at the same time, the oil in the rodless cavity of the auxiliary cylinder V12 flows back to the oil tank V1 along the A end of the electromagnetic control valve V8 through the first branch.

[0029] It should be noted that multiple auxiliary cylinders V12 are respectively connected in parallel with the first branch and the second branch to avoid interference between them. To ensure the purity of the returned oil, the oil can be filtered by an oil return filter V4 before flowing back to the oil tank V1. To ensure the working safety of the pump set, a check valve V5 can also be installed at the output end of the pump set to prevent the oil from flowing back.

[0030] In this embodiment, to further ensure the safety of the auxiliary cylinder V12 driving the load to lift, as Figure 1 shown, the lifting circuit further includes a pilot-operated check valve V9 and a pair of one-way throttle valves V10. The pilot-operated check valve V9 is installed in the first branch, and the control end of the pilot-operated check valve V9 is connected to the second branch; the two one-way throttle valves V10 are respectively installed in the first branch and the second branch; among them, the pilot-operated check valve V9 is close to the electromagnetic control valve V8.

[0031] Specifically, when the load needs to be lifted, for the rodless chamber of the auxiliary cylinder V12, the conduction direction of the hydraulic control check valve V9 is the same as the flow direction of the oil in the first branch. At the same time, the one-way throttle valve V10 on the first branch is in a non-throttling state to ensure that the oil output by the pump group can quickly flow into the rodless chamber of the auxiliary cylinder V12. For the rod chamber of the auxiliary cylinder V12, the one-way throttle valve V10 on the second branch is in a throttling state, and the lifting speed of the load driven by the auxiliary cylinder V12 can be controlled by controlling the opening degree of the one-way throttle valve V10 on the second branch. When the load needs to be lowered, for the rod chamber of the auxiliary cylinder V12, the one-way throttle valve V10 on the second branch is in a non-throttling state, which can ensure that the oil output by the pump group quickly flows into the rod chamber of the auxiliary cylinder V12. At this time, the oil pressure on the second branch can control the hydraulic control check valve V9 on the first branch to open to conduct the first branch. Furthermore, the oil in the rodless chamber of the auxiliary cylinder V12 can flow back to the fuel tank V1 along the first branch, and the one-way throttle valve V10 on the first branch is in a throttling state. The lowering speed of the load driven by the auxiliary cylinder V12 can be controlled by controlling the opening degree of the one-way throttle valve V10 on the first branch.

[0032] In this embodiment, to further ensure the safety of the auxiliary cylinder V12 driving the load to lift and lower, as Figure 1 shown, the lifting and lowering circuit further includes a pair of relief valves V11; both relief valves V11 are connected in parallel between the first branch and the second branch, and the connection directions of the two relief valves are opposite; the installation position of the relief valve V11 is on the side of the one-way throttle valve V10 close to the auxiliary cylinder V12.

[0033] Specifically, when the load is lifted, if the oil pressure in the first branch exceeds the set safety threshold, the relief valve V11 corresponding to the first branch will open at this time, so that part of the oil in the first branch flows back to the fuel tank V1 along the second branch through the relief valve V11. At the same time, when the load is lowered, if the oil pressure in the second branch exceeds the set safety threshold, the relief valve V11 corresponding to the second branch will open at this time, so that part of the oil in the second branch flows back to the fuel tank V1 along the first branch through the relief valve V11.

[0034] In this embodiment, there are various specific structures of the pressure circuit that can achieve the above functions. For the convenience of understanding, one of the structures will be described in detail below. As Figure 1As shown, the pressure circuit includes a pilot-operated check valve V16, an electromagnetic control valve V17, and an electromagnetic ball valve V18. The pilot-operated check valve V16 is installed between the A end of the electromagnetic control valve V17 and the plunger cylinder V13, and the control end of the pilot-operated check valve V16 is connected to the B end of the electromagnetic control valve V17; the P end and the T end of the electromagnetic control valve V17 are respectively connected to the pump unit and the oil tank V1; the electromagnetic ball valve V18 is connected in parallel to the pilot-operated check valve V16 and the T end of the electromagnetic control valve V17.

[0035] When it is necessary to pressurize the load, the electromagnetic control valve V17 connects the A end and the P end, so that the oil output by the pump unit can be transported from the A end of the electromagnetic control V17 through the pilot-operated check valve V16 to the inside of the plunger cylinder V13, so as to gradually pressurize the load to the set pressure; then, by controlling the electromagnetic ball valve V18 to the cut-off state, the pressure holding of the plunger cylinder V13 can be realized.

[0036] When the plunger cylinder V13 is depressurized after the load has completed its work, the electromagnetic ball valve V18 is opened. At this time, the oil in the plunger cylinder V13 will flow back to the oil tank V1 along the electromagnetic ball valve V18 through the T end of the electromagnetic control valve V17, so that the plunger cylinder V13 can be quickly depressurized to a lower pressure.

[0037] It should be noted that when the load rises under the drive of the auxiliary cylinder V12, the plunger cylinder V13 can be filled with oil and lifted through the pressure circuit under the drive of the pump unit to realize the synchronous rise of the plunger cylinder V13 and the load. When the load needs to descend, the plunger cylinder V13 needs to be depressurized first. After the depressurization is completed, the electromagnetic control valve V17 can be controlled to connect the A end and the T end, and the B end and the P end; thus, the oil output by the pump unit can open the pilot-operated check valve V16 to accelerate the return of the oil in the plunger cylinder V13. That is, part of the oil in the plunger cylinder V13 flows back to the oil tank V1 along the electromagnetic ball valve V18, and at the same time, part of the oil flows back to the oil tank V1 from the pilot-operated check valve V16 along the T end of the electromagnetic control valve V17.

[0038] It should be known that the oil in the plunger cylinder V13 can only drive the plunger cylinder V13 to move in the rising direction of the load to realize pressurization and pressure holding. When the load descends, the descending movement of the load mainly relies on the drive of the auxiliary cylinder V12. At this time, it is necessary to ensure that the oil inlet and outlet of the plunger cylinder V13 have sufficient opening to ensure that the plunger cylinder V13 will not cause great interference to the descent of the load. In this embodiment, the specification of the auxiliary cylinder V12 is significantly smaller than that of the plunger cylinder V13, so the plunger cylinder V13 needs to have a relatively large opening to ensure the descending speed of the load. In this embodiment, the main function of the pressure circuit is to control the pressurization and depressurization of the plunger cylinder V13, and the effect of the rapid return of the oil in the plunger cylinder V13 is average. Therefore, a return structure can be further set for the plunger pump V13 to ensure the descending speed of the load.

[0039] In this embodiment, as Figure 1 shown, the reflux structure capable of realizing the above functions includes a liquid filling valve V15, a control circuit and an oil return circuit. The liquid filling valve V15 is connected to the oil port position of the plunger cylinder V13, and the liquid filling valve V15 is connected to the pump group and the fuel tank V1 through the control circuit and the oil return circuit respectively. When the load is lowered, the liquid filling valve V15 is opened under the drive control of the pump group through the control circuit, and then the plunger cylinder V13 is communicated with the fuel tank V1 through the oil return circuit to accelerate the reflux of the oil.

[0040] It can be understood that the liquid filling valve V15 is actually a pilot-operated check valve, and its conduction direction is opposite to the oil inlet direction of the pressure circuit. Therefore, when the pressure circuit injects oil and pressurizes the plunger cylinder V13, the liquid filling valve V15 is in the cut-off state. Correspondingly, the oil outlet direction of the plunger cylinder V13 is also opposite to the conduction direction of the liquid filling valve V15. At this time, the liquid filling valve V15 needs to be opened through the control circuit. There are various specific structures of the control circuit capable of realizing the above functions. For the convenience of understanding, one of the structures will be described in detail below.

[0041] Specifically, as Figure 1 shown, the control circuit includes an electromagnetic control valve V20. The P end and the T end of the electromagnetic control valve V20 are connected to the pump group and the fuel tank V1 respectively, and the output end of the electromagnetic control valve V20 is connected to the control end of the liquid filling valve V15. When the load needs to be lowered, the electromagnetic control valve V20 can connect the P end with the output end. Then, the oil output by the pump group can be controlled by the electromagnetic control valve V20 from the P end along the output end to open the liquid filling valve V15, so that part of the oil in the plunger pump V13 flows back to the fuel tank V1 along the oil return circuit through the liquid filling valve V15.

[0042] It can be understood that the oil return circuit can be a pipeline structure directly connecting the liquid filling valve V15 and the fuel tank V1. Of course, in order to ensure the stable connection of the pipeline, a switching valve V22 and a shock-absorbing hose V23 can be arranged between the pipeline and the fuel tank V1.

[0043] Specifically, as Figure 1 shown, the control circuit further includes a pressure reducing valve V21 and a one-way throttle valve V19. The P end of the electromagnetic control valve V20 is connected to the pump group through the pressure reducing valve V21, and the output end of the electromagnetic control valve V20 is connected to the control end of the liquid filling valve V15 through the one-way throttle valve V19.

[0044] It should be noted that the oil pressure output by the pump group is generally relatively high, while the opening pressure requirement of the filling valve V15 is not high. Therefore, the oil pressure output from the pump group to control the opening of the filling valve V15 can be stepped down by the pressure reducing valve V21. At the same time, the opening degree of the filling valve V15 can be controlled through the one-way throttle valve V19, and thus the descending speed of the load can be adaptively adjusted along with the auxiliary cylinder V12.

[0045] In this embodiment, if the filling valve V15 fails during the process of load boosting, the oil in the pressure circuit may flow back along the filling valve V15, resulting in the load pressure not meeting the requirements. Therefore, a high-pressure ball valve V14 can be connected between the filling valve V15 and the plunger cylinder V13. When the filling valve V15 is in a normal state, the high-pressure ball valve V14 is in an open state; when the filling valve V15 is abnormal, the high-pressure ball valve V14 can be closed to ensure that the clamping force of the load can still meet the requirements.

[0046] In this embodiment, to ensure the working safety of the pump group, as Figure 1 shown, the hydraulic system further includes a relief valve V6 and an electromagnetic ball valve V7. The relief valve V6 is connected between the output end of the pump group and the fuel tank V1, and the electromagnetic ball valve V7 is connected in parallel with the relief valve V6. When the output pressure of the pump group is greater than the set safety pressure, the relief valve V6 will open, and thus part of the oil output by the pump group will directly flow back to the fuel tank V1. When the relief valve V6 is working normally, the electromagnetic ball valve V7 is in an open state; when the relief valve V6 is abnormal, the electromagnetic ball valve V7 is in a cut-off state, and at this time, the relief valve V6 can be replaced without affecting the normal operation of other oil circuits in the hydraulic system.

[0047] The basic principle, main features and advantages of the present application have been described above. Those skilled in the art should understand that the present application is not limited by the above embodiments. What is described in the above embodiments and the specification is only the principle of the present application. Without departing from the spirit and scope of the present application, the present application will have various changes and improvements, and these changes and improvements all fall within the scope of the present application claimed. The scope of protection required by the present application is defined by the appended claims and their equivalents.

Claims

1. A hydraulic system for a flat tire vulcanizer, characterized in that, It includes a plunger cylinder V13, at least one auxiliary cylinder V12, an oil tank V1, a pump unit, a lifting circuit, and a pressure circuit; Both the plunger cylinder V13 and the auxiliary cylinder V12 are connected to the load through the driving end, and the pump unit is installed on the oil tank V1; Each of the auxiliary cylinders V12 is connected to the oil tank V1 and the pump unit through the lifting circuit, and the auxiliary cylinder V12 is adapted to drive the load to lift and lower through the lifting circuit under the drive of the pump unit; The plunger cylinder V13 is connected to the oil tank V1 and the pump unit through the pressure circuit; the plunger cylinder V13 is adapted to pressurize, hold pressure, and relieve pressure on the load through the pressure circuit under the drive of the pump unit.

2. The hydraulic system for a flat tire vulcanizer according to claim 1, characterized in that, The lifting circuit includes an electromagnetic control valve V8, a first branch, and a second branch; The first ends of the first branch and the second branch are respectively connected to the A end and the B end of the electromagnetic control valve V8, and the second ends of the first branch and the second branch are respectively connected to the rodless cavity and the rod cavity of the auxiliary cylinder V12; The P end and the T of the electromagnetic control valve V8 are respectively connected to the pump unit and the oil tank V1; the electromagnetic control valve V8 drives the auxiliary cylinder V12 to drive the load to lift and lower by controlling the oil supply routes of the first branch and the second branch.

3. The hydraulic system for a flat tire vulcanizer according to claim 2, characterized in that, The lifting circuit further includes a pilot-operated check valve V9 and a pair of one-way throttle valves V10; The pilot-operated check valve V9 is installed on the first branch, and the control end of the pilot-operated check valve V9 is connected to the second branch; The two one-way throttle valves V10 are respectively installed on the first branch and the second branch; among them, the pilot-operated check valve V9 is close to the electromagnetic control valve V8.

4. The hydraulic system for a flat tire vulcanizer according to claim 3, characterized in that, The lifting circuit further includes a pair of relief valves V11; Both of the two relief valves V11 are connected in parallel between the first branch and the second branch, and the connection directions of the two relief valves are opposite; The installation position of the relief valve V11 is on the side of the one-way throttle valve V10 close to the auxiliary cylinder V12.

5. The hydraulic system for a flat tire vulcanizer according to any one of claims 1-4, characterized in that, The pressure circuit includes a pilot-operated check valve V16, an electromagnetic control valve V17, and an electromagnetic ball valve V18; The pilot-operated check valve V16 is installed between the A end of the electromagnetic control valve V17 and the plunger cylinder V13, and the control end of the pilot-operated check valve V16 is connected to the B end of the electromagnetic control valve V17; The P end and the T end of the electromagnetic control valve V17 are respectively connected to the pump unit and the oil tank V1; The electromagnetic ball valve V18 is connected in parallel to the pilot-operated check valve V16 and the T end of the electromagnetic control valve V17.

6. The hydraulic system for a flat tire vulcanizer according to claim 5, characterized in that, A filling valve V15 is connected to the oil port position of the plunger cylinder V13, and the filling valve V15 is respectively connected to the pump unit and the oil tank V1 through a control circuit and a return oil circuit; When the load is descending, the filling valve V15 is opened under the drive control of the pump unit through the control circuit, and then the plunger cylinder V13 is communicated with the oil tank V1 through the return oil circuit.

7. The hydraulic system for a flat tire vulcanizer according to claim 6, wherein, The control loop includes an electromagnetic control valve V20; the P end and the T end of the electromagnetic control valve V20 are respectively connected to the pump group and the oil tank V1, and the output end of the electromagnetic control valve V20 is connected to the control end of the filling valve V15.

8. The hydraulic system for a flat tire vulcanizer according to claim 7, characterized in that, The control loop further includes a pressure reducing valve V21 and a one-way throttle valve V19; the P end of the electromagnetic control valve V20 is connected to the pump group through the pressure reducing valve V21, and the output end of the electromagnetic control valve V20 is connected to the control end of the filling valve V15 through the one-way throttle valve V19.

9. The hydraulic system for a flat tire vulcanizer according to claim 6, characterized in that, A high-pressure ball valve V14 is also connected between the filling valve V15 and the plunger cylinder V13.

10. The hydraulic system for a flat tire vulcanizer according to claim 1, characterized in that, The hydraulic system further includes a relief valve V6 and an electromagnetic ball valve V7. The relief valve V6 is connected between the output end of the pump group and the oil tank V1, and the electromagnetic ball valve V7 is connected in parallel with the relief valve V6.

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