CN215762496U - Self-jacking hydraulic control system for transfer trolley - Google Patents
Self-jacking hydraulic control system for transfer trolley Download PDFInfo
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- CN215762496U CN215762496U CN202121527826.5U CN202121527826U CN215762496U CN 215762496 U CN215762496 U CN 215762496U CN 202121527826 U CN202121527826 U CN 202121527826U CN 215762496 U CN215762496 U CN 215762496U
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Abstract
The utility model discloses a self-jacking hydraulic control system for a transfer trolley, which comprises: the oil cylinder, the oil tank, the first control valve group, the second control valve group and the reversing valve; when the reversing valve is located at the first position, the first port and the second port are communicated, oil in the oil tank enters the rodless cavity, and when the pressure of the rodless cavity and the pressure of the rod cavity reach a first preset ratio, the first control valve group is closed, the second control valve group is communicated, and the oil in the rod cavity flows back to the oil tank, so that the piston rod moves towards the direction of the rod cavity; when the reversing valve is located at the second position, the first port and the third port are communicated, oil in the oil tank enters the rod cavity, and when the pressure of the rod cavity and the pressure of the rodless cavity reach a second preset ratio, the second control valve group is closed, the first control valve group is communicated, and the oil in the rodless cavity flows back to the oil tank, so that the piston rod moves towards the direction of the rodless cavity. The utility model can realize the lifting or descending of the oil cylinder by operating the reversing valve once.
Description
Technical Field
The utility model relates to the technical field of hydraulic control, in particular to a self-jacking hydraulic control system for a transfer trolley.
Background
Shipping needs to be considered in both the manufacturing and maintenance processes of the ship, and the conventional small-sized ship or split ship transportation can be completed mainly by a single or a plurality of flat cars. However, if a method of using a plurality of flatbeds for combined transportation is also considered in large-scale ship transportation, the difficulty of performing synchronous control is increased, the safety and reliability are reduced, the failure risk is high, and once an accident occurs, the loss of a shipowner is very large, and the method cannot be selected generally, so that a transfer system of a large-scale ship is generated. The transfer system realizes the transportation of medium and large ships through 96 transfer vehicles, can select the number of trolleys according to the size of a ship, and provides an oil source through a hydraulic station with a self-driving function, so that the lifting and the transportation of the ships off the ground are realized. Usually, a large-scale ship plant has a plurality of ship maintenance and manufacturing berths, and a transfer system is matched with each maintenance berth, so that the occupied area is large, the cost is increased, and therefore, a transfer system needs to have longitudinal walking and transverse walking functions when reaching each maintenance berth, and the problem of wheel steering needs to be considered during design.
The wheel turns to mainly by hydraulic control realization, through the hydraulic cylinder jacking, realizes transporting the dolly and leaves the track, and rethread manual operation realizes turning to. The jacking of the oil cylinder of the transfer system in the current market needs to finish the self-jacking of the transfer trolley by operating different ball valves for many times, and then finish the resetting by operating for many times in reverse. The mode is complicated to operate, misoperation is easily caused, and meanwhile due to the fact that the number of transfer vehicles is large, errors are easily caused, adverse effects are caused on ship transfer, and certain risks are caused on the transportation of the large ship.
SUMMERY OF THE UTILITY MODEL
The utility model aims to solve the problems that the lifting of an oil cylinder can be realized through multiple operations of a transfer system so as to realize the steering of a transfer vehicle, and the oil cylinder of the transfer vehicle can be reset through multiple operations. The utility model provides a self-jacking hydraulic control system for a transfer trolley, which can complete jacking or retraction of an oil cylinder through one-time operation.
In order to solve the technical problem, the embodiment of the utility model discloses a self-jacking hydraulic control system for a transfer trolley, which comprises:
the oil cylinder is internally provided with a piston rod and comprises a rod cavity and a rodless cavity, and the piston rod is positioned in the rod cavity;
an oil tank;
the first control valve group is respectively communicated with the oil tank and the rodless cavity;
the second control valve group is respectively communicated with the first control valve group, the oil tank and the rod cavity;
a reversing valve having a first port, a second port, and a third port; the first port is communicated with an oil tank, the second port is communicated with the rodless cavity, the first control valve group and the second control valve group respectively, and the third port is communicated with the rod cavity, the first control valve group and the second control valve group respectively;
when the reversing valve is in a first position, the first port is communicated with the second port, the third port is closed, oil in the oil tank enters the rodless cavity, and when the pressure of the rodless cavity and the pressure of the rod cavity reach a first preset ratio, the first control valve group is closed, the second control valve group is communicated, the oil in the rod cavity flows back to the oil tank, so that the piston rod moves towards the direction of the rod cavity;
when the reversing valve is located at the second position, the first port and the third port are communicated, the second port is closed, oil in the oil tank enters the rod cavity, and when the pressure of the rod cavity and the pressure of the rodless cavity reach a second preset ratio, the second control valve group is closed, the first control valve group is communicated, and the oil in the rodless cavity flows back to the oil tank, so that the piston rod moves towards the direction of the rodless cavity.
By adopting the technical scheme, the reversing valve is positioned at different positions by operating the reversing valve once, and the first control valve group and the second control valve group control whether the hydraulic oil in the rod cavity and the rodless cavity can flow back to the oil tank or not, so that the extension and retraction of the piston rod can be completed, and the oil cylinder is driven to lift up and descend.
According to another embodiment of the utility model, the first pilot valve group comprises a first pilot check valve and a first damping valve, and the second pilot valve group comprises a second pilot check valve and a second damping valve, wherein,
an oil inlet of the first hydraulic control one-way valve is communicated with an oil tank through a first damping valve, an oil outlet of the first hydraulic control one-way valve is respectively communicated with a rodless cavity and a second control oil port of the second hydraulic control one-way valve, and a first control oil port of the first hydraulic control one-way valve is respectively communicated with a rod cavity and an oil outlet of the second hydraulic control one-way valve;
an oil inlet of the second hydraulic control one-way valve is communicated with the oil tank through a second damping valve, an oil outlet of the second hydraulic control one-way valve is communicated with a rod cavity and a first control oil port of the first hydraulic control one-way valve respectively, and a second control oil port of the second hydraulic control one-way valve is communicated with an oil outlet of a rodless cavity and the first hydraulic control one-way valve respectively.
According to another embodiment of the present invention, the method further comprises:
the first one-way valve is arranged at the downstream of the third port, and an oil outlet of the first one-way valve is communicated with the rod cavity;
and the second one-way valve is arranged at the downstream of the second port, and an oil outlet of the second one-way valve is communicated with the rodless cavity.
According to another embodiment of the present invention, a third one-way valve is further included, upstream of the rod chamber.
According to another embodiment of the utility model, a third damping valve is arranged upstream of the reversing valve.
According to another specific embodiment of the utility model, the oil tank further comprises an overflow valve, an oil inlet of the overflow valve is communicated with the rod cavity, and an oil outlet of the overflow valve is communicated with the oil tank.
According to another embodiment of the present invention, a plurality of pressure monitors are further included for detecting the pressure of oil flowing into or out of each valve.
According to another embodiment of the utility model, the reversing valve is a three-way ball valve.
Drawings
FIG. 1 illustrates a hydraulic schematic of a self-jacking hydraulic control system for a transfer car provided in accordance with an embodiment of the present invention;
fig. 2 is a schematic diagram illustrating a connection between a first control valve group and a second control valve group according to an embodiment of the present invention.
Detailed Description
The following description of the embodiments of the present invention is provided for illustrative purposes, and other advantages and effects of the present invention will become apparent to those skilled in the art from the present disclosure. While the utility model will be described in conjunction with the preferred embodiments, it is not intended that the features of the utility model be limited to these embodiments. On the contrary, the intention of the novel description to be incorporated into the embodiments is to cover alternatives or modifications which may be extended in accordance with the appended claims. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. The utility model may be practiced without these particulars. Moreover, some of the specific details have been left out of the description in order to avoid obscuring or obscuring the focus of the present invention. It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict.
It should be noted that in this specification, like reference numerals and letters refer to like items in the following drawings, and thus, once an item is defined in one drawing, it need not be further defined and explained in subsequent drawings.
The terms "first," "second," "third," "fourth," and the like are used merely to distinguish one description from another, and are not to be construed as indicating or implying relative importance.
In the description of the present embodiment, it should be further noted that, unless explicitly stated or limited otherwise, the terms "disposed," "connected," and "connected" are to be interpreted broadly, e.g., as a fixed connection, a detachable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present embodiment can be understood in specific cases by those of ordinary skill in the art.
In order to make the objects, technical solutions and advantages of the present invention more apparent, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
In the prior art, when an oil cylinder extends out and jacks, a self-jacking control system needs to open a rod cavity oil return ball valve, close a rodless cavity oil return ball valve and operate a three-way ball valve to realize the extension of the oil cylinder. When the valve retracts, the rodless cavity oil return ball valve is opened first, then the rod cavity oil return ball valve is closed, and then the three-way ball valve is operated. The switching among different ball valves is needed for realizing the operation.
As shown in fig. 1, an embodiment of the present invention provides a self-jacking hydraulic control system for a transfer car, comprising:
the oil cylinder 1 is internally provided with a piston rod 13, the oil cylinder 1 comprises a rod cavity 15 and a rodless cavity 14, and the piston rod 13 is positioned in the rod cavity 15;
an oil tank 2;
the first control valve group 3 is respectively communicated with the oil tank 2 and the rodless cavity 14;
the second control valve group 4 is respectively communicated with the first control valve group 3, the oil tank 2 and the rod cavity 15;
a directional valve 5 having a first port 5a, a second port 5b and a third port 5 c; the first port 5a is communicated with the oil tank 2, the second port 5b is communicated with the rodless cavity 14, the first control valve group 3 and the second control valve group 4 respectively, and the third port 5c is communicated with the rod cavity 15, the first control valve group 3 and the second control valve group 4 respectively;
when the reversing valve 5 is in the first position, the first port 5a and the second port 5b are communicated, the third port 5c is closed, oil in the oil tank 2 enters the rodless cavity 14, and when the pressure of the rodless cavity 14 and the pressure of the rod cavity 15 reach a first preset ratio, the first control valve group 3 is closed, the second control valve group 4 is communicated, the oil in the rod cavity 15 flows back to the oil tank 2, so that the piston rod 13 moves towards the rod cavity 15;
when the reversing valve 5 is in the second position, the first port 5a and the third port 5c are communicated, the second port 5b is closed, oil in the oil tank 2 enters the rod cavity 15, and when the pressure of the rod cavity 15 and the pressure of the rodless cavity 14 reach a second preset ratio, the second control valve group 4 is closed, the first control valve group 3 is communicated, and the oil in the rodless cavity 14 flows back to the oil tank 2, so that the piston rod 13 moves towards the direction of the rodless cavity 14.
Specifically, in the present embodiment, the oil cylinder 1 includes a cylinder 11, a piston 12, and a piston rod 13 connected to the piston 12. Specifically, the piston 12 is provided in the cylinder 11 and divides the internal space of the cylinder 11 into two chambers, one of which is provided with the piston rod 13, which is referred to as a rod chamber 15 in the present embodiment, and the other of which is free of the piston rod 13, which is referred to as a rodless chamber 14.
In the embodiment, when the hydraulic oil is continuously injected into the rodless cavity 14 and the hydraulic oil in the rod cavity 15 flows out, the piston rod 13 extends out, and at the moment, the oil cylinder 1 is in a jacking state, so that the transfer trolley can be jacked; when the hydraulic oil is continuously injected into the rod cavity 15 and the hydraulic oil in the rodless cavity 14 flows out, the piston rod 13 retracts, and at the moment, the oil cylinder 1 is in a descending state, so that the transfer trolley can be reset.
By adopting the technical scheme, the reversing valve 5 is positioned at different positions by operating the one-time reversing valve 5, the first control valve group 3 and the second control valve group 4 control the rod cavity 15 and the rodless cavity 14, one of the cavities takes oil, the other cavity takes oil out, the piston rod 13 can be stretched out and retracted, and then the oil cylinder 1 is driven to lift up and descend.
Specifically, in the present embodiment, the direction valve 5 is a three-way ball valve. The first port 5a is an oil inlet, when a valve core of the reversing valve 5 is at a first position, the second port 5b is an oil outlet, and the third port 5c is closed; when the spool of the direction valve 5 is in the second position, the second port 5b is closed, and the third port 5c is an oil outlet. As shown in fig. 1, the first port 5a and the third port 5c are in a conductive state when the direction valve 5 is in the second position.
More specifically, in the present embodiment, the self-lifting hydraulic control system further includes a hydraulic pump 21 disposed between the oil tank 2 and the direction switching valve 5, and a fourth check valve 22 disposed on an oil path between the hydraulic pump 21 and the direction switching valve 5, an oil outlet of the fourth check valve 22 facing the direction switching valve 5. The hydraulic oil in the oil tank 2 is drawn into the line by the hydraulic pump 21. A fourth check valve 22 is provided on an oil path between the directional valve 5 and the hydraulic pump 21 to prevent a backflow of the hydraulic oil.
In the embodiment, an oil inlet of the first control valve group 3 is communicated with the oil tank 2, an oil outlet is communicated with the rodless cavity 14, and a first control oil port is communicated with the rod cavity 15; an oil inlet of the second control valve group 4 is communicated with the oil tank 2, an oil outlet of the second control valve group is communicated with the rod cavity 15, and a second control oil port is communicated with the rodless cavity 14. That is, the rodless cavity 14 is respectively communicated with the oil outlet of the first control valve group 3 and the second control oil port of the second control valve group 4; the rod cavity 15 is respectively communicated with a first control oil port of the first control valve group 3 and an oil outlet of the second control valve group 4. It should be noted that the oil inlet and the oil outlet of the first control valve group 3 refer to oil ports when the first control valve group 3 is in forward conduction, that is, when the ratio of the pressure of the first control oil port of the first control valve group 3 to the pressure of the oil outlet does not reach a preset ratio, oil is fed from the oil inlet, and the oil is discharged from the oil outlet, but when the pressure of the first control oil port and the pressure of the oil outlet reach the preset ratio, the first control valve group 3 is in reverse conduction, that is, oil is fed from the oil outlet, and oil is discharged from the oil inlet. The second control valve block 4 has the same principle as the first control valve block 3.
When the oil cylinder 1 is in a jacking position to lift the transfer car, the reversing valve 5 is operated to enable the reversing valve 5 to be in a state that the first port 5a and the second port 5b are communicated, the hydraulic pump 21 pumps hydraulic oil in the oil tank 2 into the pipeline, the hydraulic oil enters the rodless cavity 14 through the reversing valve 5, at the moment, the second control valve group 4 is closed, hydraulic oil in the rod cavity 15 cannot flow out, and therefore the rod cavity 15 is in a pressure maintaining state. Along with hydraulic oil gets into in the rodless chamber 14, the pressure in the rodless chamber 14 increases gradually, because the first control hydraulic fluid port of first control valves 3 and have the pole chamber 15 to communicate, the oil-out of first control valves 3 and rodless chamber 14 intercommunication, consequently when the pressure ratio of the first control hydraulic fluid port of first control valves 3 and the oil-out of first control valves 3 is first predetermined ratio, first control valves 3 close, second control valves 4 switches on, make to have the hydraulic oil in the pole chamber 15 to flow back to oil tank 2, thereby realize stretching out of piston rod 13, jack-up hydro-cylinder 1, thereby can be with the transfer car (buggy) jack-up. On the contrary, when the cylinder 1 is to be in the retracted position to reset the transfer vehicle, the directional control valve 5 is operated to make the directional control valve 5 in a state where the first port 5a and the third port 5c are communicated, the hydraulic pump 21 pumps the hydraulic oil in the oil tank 2 into the pipeline, the hydraulic oil enters the rod chamber 15 through the directional control valve 5, and at this time, the first control valve group 3 is closed, the hydraulic oil in the rod-less chamber 14 does not flow out, and thus the rod-less chamber 14 is in the pressure maintaining state. As the hydraulic oil enters the rod cavity 15, the pressure in the rod cavity 15 gradually increases, and the second control oil port of the second control valve group 4 is communicated with the rodless cavity 14, and the oil outlet of the second control valve group 4 is communicated with the rod cavity 15, when the pressure ratio of the second control oil port of the second control valve group 4 to the oil outlet of the second control valve group 4 reaches a second preset ratio, the second control valve group 4 is closed, the first control valve group 3 is conducted, so that the hydraulic oil in the rodless cavity 14 flows back to the oil tank 2, the retraction of the piston rod 13 is realized, the oil cylinder 1 descends, and the transfer trolley can slowly descend along with the oil cylinder 1 according to the self weight.
It should be noted that, in the present invention, the first preset ratio and the second preset ratio may be the same or different, and the present invention is not limited to this, and may be selected according to actual needs.
Further, in the present embodiment, the first pilot valve group 3 includes a first pilot check valve 31 and a first damping valve 32, and the second pilot valve group 4 includes a second pilot check valve 41 and a second damping valve 42, wherein,
an oil inlet a1 of the first pilot-controlled check valve 31 is communicated with the oil tank 2 through the first damping valve 32, an oil outlet b1 of the first pilot-controlled check valve 31 is respectively communicated with the rodless cavity 14 and a second control oil port c2 of the second pilot-controlled check valve 41, and a first control oil port c1 of the first pilot-controlled check valve 31 is respectively communicated with the rod cavity 15 and an oil outlet b2 of the second pilot-controlled check valve 41;
an oil inlet a2 of the second hydraulic control check valve 41 is communicated with the oil tank 2 through the second damping valve 42, an oil outlet b2 of the second hydraulic control check valve 41 is respectively communicated with the rod cavity 15 and a first control oil port c1 of the first hydraulic control check valve 31, and a second control oil port c2 of the second hydraulic control check valve 41 is respectively communicated with the rodless cavity 14 and an oil outlet b1 of the first hydraulic control check valve 31.
Specifically, as shown in fig. 2, the first pilot operated check valve 31 has an oil inlet a1, an oil outlet b1 and a first control oil port c1, and the second pilot operated check valve 41 has an oil inlet a2, an oil outlet b2 and a second control oil port c 2. For the first pilot-controlled check valve 31, when the pressure of the first pilot oil port c1 and the pressure of the oil outlet b1 do not reach a preset ratio, that is, the pressure guide ratio of the first pilot-controlled check valve 31 is not reached, the first pilot-controlled check valve 31 is conducted in the forward direction, oil is fed from the oil inlet a1, and oil is discharged from the oil outlet b 1; when the pressure of the first control oil port c1 and the pressure of the oil outlet b1 reach a preset ratio, namely the pressure guide ratio of the first hydraulic control one-way valve 31 is reached, the first hydraulic control one-way valve 31 is conducted in the reverse direction, oil is fed from the oil outlet b1, and oil is discharged from the oil inlet a 1. The second pilot check valve 41 is the same as the first pilot check valve 31.
Specifically, in the present embodiment, the first preset ratio is the pilot pressure ratio of the second pilot check valve 41, and the second preset ratio is the pilot pressure ratio of the first pilot check valve 31. In a specific embodiment of the present invention, the pressure guiding ratio of the first pilot-controlled check valve 31 and the second pilot-controlled check valve 41 is 3:1, that is, when the pressure of the pilot oil port reaches 1/3 of the pressure of the oil outlet, the first pilot-controlled check valve 31 and the second pilot-controlled check valve 41 are conducted in reverse, the hydraulic oil enters from the oil outlet, and the hydraulic oil flows out from the oil inlet.
When the piston rod 13 of the oil cylinder 1 is extended, the hydraulic oil enters the rodless cavity 14, and at this time, because the pressure of the first control oil port c1 of the first pilot-controlled check valve 31 is greater than the pressure of the oil outlet b1, the first pilot-controlled check valve 31 is in an open state, and the hydraulic oil in the rodless cavity 14 directly returns to the oil tank 2. However, since the first damping valve 32 is provided in front of the oil inlet a1 of the first pilot-operated check valve 31, the first damping valve 32 restricts the flow rate of the hydraulic oil, so that the pressure in the rodless chamber 14 gradually increases while the pressure in the rod chamber 15 is in the pressure maintaining state, and thus a pressure difference is generated between the rod chamber 15 and the rodless chamber 14. Because the second control oil port c2 of the second hydraulic control check valve 41 is communicated with the rodless cavity 14, the oil outlet b2 is communicated with the rod cavity 15, when the pressure difference between the rod cavity 15 and the rodless cavity 14 reaches the pressure guide ratio of the second hydraulic control check valve 41, the second hydraulic control check valve 41 is conducted reversely, the hydraulic oil in the rod cavity 15 flows back to the oil tank 2 through the second hydraulic control check valve 41, the pressure in the rod cavity 15 is reduced to 0, and at this time, the pressure of the first control oil port c1 of the first hydraulic control check valve 31 is reduced to 0, so that the first hydraulic control check valve 31 is closed, and the automatic extension of the oil cylinder 1 is realized. On the contrary, when the piston rod 13 of the oil cylinder 1 is to be retracted, the hydraulic oil enters the rod chamber 15, and at this time, since the pressure of the second control oil port c2 of the second hydraulic check valve 41 is greater than the pressure of the oil outlet b2, the second hydraulic check valve 41 is in an open state, and the hydraulic oil in the rod chamber 15 directly returns to the oil tank 2. However, since the second damping valve 42 is provided in front of the oil inlet a2 of the second hydraulic check valve 41, the second damping valve 42 restricts the flow rate of the hydraulic oil, so that the pressure in the rod chamber 15 gradually increases while the pressure in the rodless chamber 14 is in the pressure maintaining state, and thus a pressure difference is generated between the rodless chamber 14 and the rod chamber 15. Because the first control oil port c1 of the first pilot-controlled check valve 31 is communicated with the rod cavity 15, and the oil outlet b1 is communicated with the rodless cavity 14, when the pressure difference between the rodless cavity 14 and the rod cavity 15 reaches the pressure guide ratio of the first pilot-controlled check valve 31, the first pilot-controlled check valve 31 is conducted reversely, the hydraulic oil in the rodless cavity 14 flows back to the oil tank 2 through the first pilot-controlled check valve 31, the pressure in the rodless cavity 14 is reduced to 0, and at this time, the pressure of the second control oil port c2 of the second pilot-controlled check valve 41 is reduced to 0, so that the second pilot-controlled check valve 41 is closed, and the automatic retraction of the oil cylinder 1 is realized.
Further, the hydraulic pump also comprises a first one-way valve 61 which is arranged at the downstream of the third port 5c, and an oil outlet of the first one-way valve 61 is communicated with the rod cavity 15; and a second check valve 62 provided downstream of the second port 5b, an oil outlet of the second check valve 62 communicating with the rodless chamber 14. By adopting the technical scheme, the first one-way valve 61 is arranged on an oil path between the third port 5c of the reversing valve 5 and the rod cavity 15 to prevent the hydraulic oil in the rod cavity 15 from flowing back to the oil tank 2 from the reversing valve 5, and the second one-way valve 62 is arranged on an oil path between the second port 5b of the reversing valve 5 and the rodless cavity 14 to prevent the hydraulic oil in the rodless cavity 14 from flowing back to the oil tank 2 through the reversing valve 5.
Further, a third check valve 63 is included, upstream of the rod chamber 15. Specifically, an oil inlet of the third check valve 63 is communicated with an oil outlet of an automatic cabinet (not shown), and an oil outlet of the third check valve 63 is communicated with the rod chamber 15. By adopting the technical scheme, in the walking process of the transfer trolley, certain hydraulic oil is kept in the rod cavity 15, so that the piston rod 13 can be kept in a retraction state, and the piston rod 13 is prevented from falling to damage the oil cylinder 1 and further damage the transfer trolley.
Further, a third damping valve 51 is provided upstream of the direction valve 5.
It should be noted that, in the present invention, the first damping valve 32, the second damping valve 42 and the third damping valve 51 are used for adjusting the flow rate of the hydraulic oil, and the sizes of the damping holes of the damping valves may be set according to different system requirements, and of course, the sizes of the damping holes of the three damping valves may be set to be the same or different. In one embodiment of the present invention, the damping holes are all 2mm in size.
Further, the oil-saving device further comprises a first overflow valve 7, an oil inlet of the first overflow valve 7 is communicated with the rod cavity 15, and an oil outlet of the first overflow valve 7 is communicated with the oil tank 2. By adopting the technical scheme, the overhigh pressure in the rod cavity 15 is prevented, and when the overhigh pressure in the rod cavity 15 exists, the oil in the rod cavity 15 flows back to the oil tank 2 through the first overflow valve 7.
Specifically, a second relief valve 23 is also provided upstream of the selector valve 5. More specifically, the oil inlet of the second relief valve 23 communicates with the oil outlet of the fourth check valve 22, and the oil outlet of the second relief valve 23 communicates with the oil tank 2. By adopting the technical scheme, the pressure of the hydraulic oil entering the reversing valve 5 is prevented from being too high.
Further, a plurality of pressure monitors, which may be pressure sensors, pressure relays, etc., are included for detecting the pressure of the oil flowing into or out of the respective valves. By adopting the technical scheme, a plurality of monitoring points are arranged, so that when the system fails, the fault point can be found in time. Specifically, in the present embodiment, the plurality of pressure monitors includes a first pressure monitor 81, a second pressure monitor 82, a third pressure monitor 83, a fourth pressure monitor 84, and a fifth pressure monitor 85. Wherein, the first pressure monitor 81 is connected with the oil tank 2 and is used for detecting the pressure of the oil tank 2; a second pressure monitor 82 is connected to the rod chamber 15 for detecting the pressure within the rod chamber 15; a third pressure monitor 83 is connected to the rodless chamber 14 for detecting the pressure within the rodless chamber 14; the fourth pressure monitor 84 is connected with the oil inlet of the third one-way valve 63 and is used for detecting the pressure of the hydraulic oil from the automatic cabinet; the fifth pressure monitor 85 is connected to the oil inlet of the directional control valve 5, and is configured to detect the pressure of the hydraulic oil entering the directional control valve 5.
The working principle of the utility model is as follows:
jacking operation: when the change valve 5 is operated to enable the oil cylinder 1 to be in the jacking position, the first port 5a and the second port 5b of the change valve 5 are communicated, the third port 5c is closed, hydraulic oil enters an oil path from the oil tank 2 through the hydraulic pump 21 and enters the rodless cavity 14 of the oil cylinder 1 after passing through the second port 5b of the change valve 5, and at the moment, because the oil cylinder 1 is in the retraction state before, the pressure in the rod cavity 15 is in a pressure maintaining state. Since the oil outlet b1 of the first pilot-controlled check valve 31 is communicated with the rodless chamber 14, and the first control oil port c1 of the first pilot-controlled check valve 31 is communicated with the rod chamber 15, the oil outlet b1 is the pressure in the rodless chamber 14, and the first control oil port c1 is the pressure in the rod chamber 15. Because the pressure in the rod chamber 15 is in the pressure maintaining state, the pressure of the first control oil port c1 is greater than the pressure of the oil outlet b1, so that the first pilot-controlled check valve 31 is directly conducted in the reverse direction, at this time, one path of the hydraulic oil coming out from the second port 5b of the reversing valve 5 enters the rodless chamber 14, and the other path of the hydraulic oil directly returns to the oil tank 2 from the first pilot-controlled check valve 31, and at this time, the pressure in the rodless chamber 14 cannot be built to push the piston rod 13 to extend. However, since the first damping valve 32 is provided in front of the oil inlet a1 of the first pilot-operated check valve 31, the first damping valve 32 restricts the flow rate of the hydraulic oil flowing out in the reverse direction from the first pilot-operated check valve 31, so that a back pressure is generated at the oil outlet b1 of the first pilot-operated check valve 31, which is the pressure in the rodless chamber 14, that is, the pressure in the rodless chamber 14 gradually increases. When the pressure in the rodless cavity 14 reaches 1/3 times of the pressure in the rod cavity 15, because the oil outlet b2 of the second hydraulic control one-way valve 41 is communicated with the rod cavity 15, and the second control oil port c2 of the second hydraulic control one-way valve 41 is communicated with the rodless cavity 14, that is, when the pressure ratio of the second control oil port c2 to the oil outlet b2 is 1:3, the second hydraulic control one-way valve 41 is conducted reversely, the pressure in the rod cavity 15 is completely released, the pressure drops to 0, meanwhile, a loop is formed between the rod cavity 15 and the oil tank 2, and the hydraulic oil directly returns to the oil tank 2; at this time, since the pressure in the rod chamber 15 is almost reduced to 0, and the pressure of the first pilot port c1 of the first pilot operated check valve 31 is 0, the first pilot operated check valve 31 is closed, and the pressure in the rodless chamber 14 is directly raised to the preset pressure, so that the oil cylinder 1 is jacked up, and the trolley jacking control is completed.
Descending operation: when the change valve 5 is operated to make the oil cylinder 1 in the descending position, the first port 5a and the third port 5c of the change valve 5 are conducted, the second port 5b is closed, the hydraulic oil enters the oil path from the oil tank 2 through the hydraulic pump 21 and enters the rod chamber 15 of the oil cylinder 1 after passing through the third port 5c of the change valve 5, and at this time, the pressure in the rodless chamber 14 is in the pressure maintaining state because the oil cylinder 1 is in the extending state before. Since the oil outlet b2 of the second hydraulic check valve 41 is communicated with the rod chamber 15, and the second control oil port c2 of the second hydraulic check valve 41 is communicated with the rodless chamber 14, the oil outlet b2 is the pressure in the rod chamber 15, and the second control oil port c2 is the pressure in the rodless chamber 14. Because the pressure in the rodless cavity 14 is in a pressure maintaining state, the pressure of the second control oil port c2 is greater than the pressure of the oil outlet b2, so that the second hydraulic control check valve 41 is directly conducted in the reverse direction, at this time, one path of hydraulic oil coming out from the third port 5c of the reversing valve 5 enters the rod cavity 15, the other path of hydraulic oil directly returns to the oil tank 2 from the second hydraulic control check valve 41, and at this time, the pressure cannot be built in the rod cavity 15 to push the piston rod 13 to retract. However, since the second damping valve 42 is provided in front of the oil inlet a2 of the second check valve 41, the second damping valve 42 restricts the flow rate of the hydraulic oil flowing out in the reverse direction from the second check valve 41, so that a back pressure is generated at the oil outlet b2 of the second check valve 41, and this pressure is the pressure in the rod chamber 15, that is, the pressure in the rod chamber 15 gradually increases. When the pressure in the rod cavity 15 reaches 1/3 times of the pressure in the rodless cavity 14, because the oil outlet b1 of the first pilot-controlled check valve 31 is communicated with the rodless cavity 14, the first control oil port c1 of the first pilot-controlled check valve 31 is communicated with the rod cavity 15, that is, when the pressure ratio of the first control oil port c1 to the oil outlet b1 is 1:3, the first pilot-controlled check valve 31 is conducted reversely, then the pressure in the rodless cavity 14 is completely released, the pressure almost drops to 0, meanwhile, a loop is formed between the rodless cavity 14 and the oil tank 2, and the hydraulic oil directly returns to the oil tank 2; at this time, since the pressure in the rodless chamber 14 is almost reduced to 0 and the pressure of the second control port c2 of the second hydraulic check valve 41 is 0, the second hydraulic check valve 41 is closed, and the pressure in the rod chamber 15 is directly raised to the preset pressure, so that the cylinder 1 is retracted, and the trolley can finish the descent by its own weight.
According to the self-jacking hydraulic control system for the transfer trolley, the jacking or descending of the oil cylinder 1 can be completed only by operating the reversing valve 5 once, the convenience of operation and the reliability of the system are improved by a simple operation mode, and the risk of the transfer system is reduced.
While the utility model has been shown and described with reference to certain preferred embodiments thereof, it will be understood by those skilled in the art that the foregoing is a more detailed description of the utility model, taken in conjunction with the specific embodiments thereof, and that no limitation of the utility model is intended thereby. Various changes in form and detail, including simple deductions or substitutions, may be made by those skilled in the art without departing from the spirit and scope of the utility model.
Claims (8)
1. A self-jacking hydraulic control system for a transfer car (buggy), comprising:
the piston rod is arranged in the oil cylinder, the oil cylinder comprises a rod cavity and a rodless cavity, and the piston rod is positioned in the rod cavity;
an oil tank;
the first control valve group is respectively communicated with the oil tank and the rodless cavity;
the second control valve group is respectively communicated with the first control valve group, the oil tank and the rod cavity;
a reversing valve having a first port, a second port, and a third port; the first port is communicated with the oil tank, the second port is communicated with the rodless cavity, the first control valve group and the second control valve group respectively, and the third port is communicated with the rod cavity, the first control valve group and the second control valve group respectively;
when the reversing valve is located at a first position, the first port is communicated with the second port, the third port is closed, oil in the oil tank enters the rodless cavity, and when the pressure of the rodless cavity and the pressure of the rod cavity reach a first preset ratio, the first control valve group is closed, the second control valve group is communicated, and the oil in the rod cavity flows back to the oil tank so as to enable the piston rod to extend out;
when the reversing valve is located at a second position, the first port is communicated with the third port, the second port is closed, oil in the oil tank enters the rod cavity, and when the pressure of the rod cavity and the pressure of the rodless cavity reach a second preset ratio, the second control valve group is closed, the first control valve group is communicated, and the oil in the rodless cavity flows back to the oil tank, so that the piston rod retracts.
2. The self-jacking hydraulic control system for a transfer car (buggy) of claim 1, wherein said first set of pilot valves includes a first pilot operated check valve and a first damping valve, and said second set of pilot valves includes a second pilot operated check valve and a second damping valve, wherein,
an oil inlet of the first hydraulic control one-way valve is communicated with the oil tank through the first damping valve, an oil outlet of the first hydraulic control one-way valve is respectively communicated with the rodless cavity and a second control oil port of the second hydraulic control one-way valve, and a first control oil port of the first hydraulic control one-way valve is respectively communicated with the rod cavity and the oil outlet of the second hydraulic control one-way valve;
an oil inlet of the second hydraulic control one-way valve is communicated with the oil tank through the second damping valve, an oil outlet of the second hydraulic control one-way valve is communicated with the rod cavity and a first control oil port of the first hydraulic control one-way valve respectively, and a second control oil port of the second hydraulic control one-way valve is communicated with an oil outlet of the rodless cavity and the first hydraulic control one-way valve respectively.
3. The self-jacking hydraulic control system for a transfer car (buggy) of claim 2, further comprising:
the first one-way valve is arranged at the downstream of the third port, and an oil outlet of the first one-way valve is communicated with the rod cavity;
and the second one-way valve is arranged at the downstream of the second port, and an oil outlet of the second one-way valve is communicated with the rodless cavity.
4. The self-jacking hydraulic control system for a transfer car (buggy) of claim 3, further comprising a third one-way valve located upstream of said rod chamber.
5. The self-jacking hydraulic control system for a transfer car (buggy) of claim 1, wherein a third damping valve is further provided upstream of the reversing valve.
6. The self-jacking hydraulic control system for transfer trucks of claim 1, further comprising an overflow valve, an oil inlet of said overflow valve being in communication with said rod chamber and an oil outlet of said overflow valve being in communication with said oil tank.
7. The self-jacking hydraulic control system for a transfer car (buggy) of any one of claims 1 to 6, further comprising a plurality of pressure monitors for detecting the pressure of oil flowing into or out of each valve.
8. The self-jacking hydraulic control system for transfer trucks of claim 1, wherein said reversing valve is a three-way ball valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121527826.5U CN215762496U (en) | 2021-07-06 | 2021-07-06 | Self-jacking hydraulic control system for transfer trolley |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121527826.5U CN215762496U (en) | 2021-07-06 | 2021-07-06 | Self-jacking hydraulic control system for transfer trolley |
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| Publication Number | Publication Date |
|---|---|
| CN215762496U true CN215762496U (en) | 2022-02-08 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202121527826.5U Active CN215762496U (en) | 2021-07-06 | 2021-07-06 | Self-jacking hydraulic control system for transfer trolley |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN215762496U (en) |
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2021
- 2021-07-06 CN CN202121527826.5U patent/CN215762496U/en active Active
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