CN215171162U - Improved hydraulic system of double-hoisting-point gate hoist - Google Patents
Improved hydraulic system of double-hoisting-point gate hoist Download PDFInfo
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- CN215171162U CN215171162U CN202121202406.XU CN202121202406U CN215171162U CN 215171162 U CN215171162 U CN 215171162U CN 202121202406 U CN202121202406 U CN 202121202406U CN 215171162 U CN215171162 U CN 215171162U
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Abstract
The utility model discloses a modified double-hanging-point gate hoist hydraulic system, including oil pump, second cartridge valve and the DT2, third cartridge valve and DT3, pneumatic cylinder and the other valves of jar and the sequence valve that link to each other, the other valves of jar include the hydraulic control check valve, the oil tank is connected to the oil inlet of oil pump, the oil inlet of second cartridge valve and third cartridge valve is connected to the oil outlet, the oil inlet of sequence valve and the control mouth of hydraulic control check valve are connected to the oil outlet of second cartridge valve, the rodless chamber of pneumatic cylinder is connected to the oil outlet of sequence valve, draining port connects the oil tank, the oil inlet of hydraulic control check valve is connected to the oil outlet of third cartridge valve, the rodless chamber of pneumatic cylinder is connected to the oil outlet of hydraulic control check valve, the rodless chamber of draining port connection pneumatic cylinder; the problem that the double-hoisting-point gate slides downwards when the gate closing process stops is solved by communicating a control oil path between the second cartridge valve and a control port of the hydraulic control one-way valve with a second oil outlet of a second electromagnetic directional valve in the DT 2.
Description
Technical Field
The utility model relates to a hydraulically controlled technical field especially relates to a two hoisting point gate headstock gear hydraulic system of modified.
Background
In large-scale water conservancy and hydropower engineering, the double-hoisting-point hydraulic hoist is widely applied to opening and closing large and medium gates, and has very important significance for realizing allocation control of water resources and preventing and controlling natural disasters. The working gate of the currently used double-hoisting-point large and medium gate generally adopts a two-way cartridge valve combination type hydraulic principle to control a hydraulic cylinder to realize the opening and closing of the gate, a hydraulic system controls the piston rod of the hydraulic cylinder to extend downwards, then the gate is closed, and the hydraulic system controls the piston rod of the hydraulic cylinder to retract upwards, then the gate is opened; however, when the gate is stopped to be closed in the closing process, the double-hoisting-point working gate is easy to slide downwards, and the opening control precision of the gate is influenced.
SUMMERY OF THE UTILITY MODEL
Technical problem to be solved
Based on the problem, the utility model provides a two hoisting point gate headstock gear hydraulic system of modified solves and closes the gate in-process and stops to close the problem of gliding easily.
(II) technical scheme
Based on the technical problem, the utility model provides an improved hydraulic system of a double-hoisting-point gate hoist, which comprises an oil pump, a second cartridge valve and a second directional control valve set DT2 connected with the second cartridge valve, a third cartridge valve and a third directional control valve set DT3 connected with the third cartridge valve, a hydraulic cylinder and a cylinder side valve set of the hydraulic cylinder, and a sequence valve, the cylinder side valve group comprises a hydraulic control one-way valve, an oil inlet of the oil pump is connected with an oil tank, an oil outlet of the oil pump is connected with oil inlets of the second cartridge valve and the third cartridge valve, the oil outlet of the second cartridge valve is connected with the oil inlet of the sequence valve and the control port of the hydraulic control one-way valve, the oil outlet of the sequence valve is connected with the rodless cavity of the hydraulic cylinder, the oil drain port is connected with the oil tank, the oil outlet of the third cartridge valve is connected with the oil inlet of the hydraulic control one-way valve, an oil outlet of the hydraulic control one-way valve is connected with a rod cavity of the hydraulic cylinder, and an oil drainage port is connected with a rodless cavity of the hydraulic cylinder; DT2 includes second electromagnetic directional valve and second shuttle valve, an oil inlet of second shuttle valve is connected the oil inlet of second cartridge valve, another oil inlet is connected the oil-out of second cartridge valve, the oil-out is connected the oil inlet of second electromagnetic directional valve, the oil return opening of second electromagnetic directional valve connects the oil tank, first oil-out is connected the control port of second cartridge valve, the second oil-out is connected the oil inlet of sequence valve.
Furthermore, the hydraulic system further comprises a first cartridge valve and a first pressure control valve group DT1 connected with the first cartridge valve, a fourth cartridge valve and a fourth pressure control valve group DT4 connected with the fourth cartridge valve, a fifth cartridge valve and a fifth pressure control valve group DT5 connected with the fifth cartridge valve, an oil inlet of the first cartridge valve is connected with an oil outlet of the oil pump, oil outlets of the first cartridge valve and the fourth cartridge valve are connected with an oil tank, an oil inlet of the fourth cartridge valve is connected with an oil outlet of the fifth cartridge valve, and an oil inlet of the fifth cartridge valve is connected with an oil inlet of the hydraulic control one-way valve.
Furthermore, the DT1 includes a first electromagnetic directional valve and a first overflow valve, an oil inlet of the first electromagnetic directional valve, an oil inlet of the first overflow valve and a control port of the first cartridge valve are connected to an oil inlet of the first cartridge valve, and an oil return port of the first electromagnetic directional valve, a second oil outlet and an oil outlet of the first overflow valve are connected to an oil tank; the DT4 comprises a fourth electromagnetic reversing valve and a fourth overflow valve, the DT5 comprises a fifth electromagnetic reversing valve and a fifth overflow valve, and the connection relationship between the DT4 and the DT5 is the same as the connection relationship between the electromagnetic reversing valve, the overflow valve and the cartridge valve corresponding to the DT 1.
Furthermore, DT3 includes third electromagnetic directional valve and third shuttle valve, an oil inlet of third shuttle valve is connected the oil inlet of third cartridge valve, another oil inlet is connected the oil-out of third cartridge valve, the oil-out is connected the oil inlet of third electromagnetic directional valve, the oil return port of third electromagnetic directional valve connects the oil tank, first oil-out is connected the control mouth of third cartridge valve.
Furthermore, the hydraulic system further comprises a one-way valve, an oil inlet of the one-way valve is connected with an oil tank, and an oil outlet of the one-way valve is connected with an oil outlet of the sequence valve.
Further, the oil pump includes first oil pump and second oil pump, first oil pump and second oil pump link to each other with the motor respectively.
Furthermore, the cylinder side valve group also comprises a safety overflow valve, wherein an oil inlet of the safety overflow valve is connected with a rod cavity of the hydraulic cylinder, and an oil outlet of the safety overflow valve is connected with a rodless cavity of the hydraulic cylinder.
Furthermore, the hydraulic cylinders comprise a first hydraulic cylinder and a second hydraulic cylinder which act on two ends of the double-hoisting-point gate, and an oil way at an oil outlet of the third cartridge valve is divided and is respectively connected with a hydraulic control one-way valve in a cylinder side valve group of the first hydraulic cylinder and a hydraulic control one-way valve in a cylinder side valve group of the second hydraulic cylinder.
Further, the set pressure of the first overflow valve is 22.5MPa, the set pressure of the fourth overflow valve is 1.0MPa, and the set pressure of the fifth overflow valve is 21.5 MPa; the first electromagnetic directional valve, the fourth electromagnetic directional valve and the fifth electromagnetic directional valve are communicated with the port P and the port B when the power is off, the port T is communicated with the port A, the port P is communicated with the port A when the power is on, and the port T is communicated with the port B.
Furthermore, the second electromagnetic directional valve and the third electromagnetic directional valve are communicated with the port P and the port A when the power is off, the port T is communicated with the port B, the port P is communicated with the port B when the power is on, and the port T is communicated with the port A; the set pressure of the sequence valve is 6 MPa.
(III) advantageous effects
The above technical scheme of the utility model has following advantage:
(1) the utility model discloses in time discharge the control oil of the control port of pilot operated check valve through the second oil-out of second electromagnetic directional valve, do not change the control mode among the prior art, but can effectively solve the gate and close the in-process and can't stop in time, namely the piston rod continues to stretch out downwards, causes the problem that two hoisting point gates glide, and gate closing and opening also can normally go on through hydraulic system;
(2) the pressure control valve group ensures that the pressure of the oil way does not exceed the set pressure of the overflow valve, and ensures the safe and stable operation of the hydraulic system; the rod cavity is also protected by a safety overflow valve;
(3) the utility model discloses a differential extension can be realized to hydraulic circuit for the piston rod fast action targets in place and the withdrawal, and can in time mend oil, prevents the emergence of suction phenomenon.
Drawings
The features and advantages of the invention will be more clearly understood by reference to the accompanying drawings, which are schematic and should not be understood as imposing any limitation on the invention, in which:
fig. 1 is a hydraulic schematic diagram of a hydraulic system of a double-hoisting-point gate hoist before improvement of an embodiment of the present invention when the gate closing operation is finished;
fig. 2 is a hydraulic schematic diagram of a hydraulic system of an improved double-hoisting-point gate hoist according to an embodiment of the present invention when closing a gate;
fig. 3 is a hydraulic schematic diagram of the improved hydraulic system of the double-hoisting-point gate hoist according to the embodiment of the present invention when the gate closing operation is stopped;
fig. 4 is a hydraulic schematic diagram of the improved hydraulic system of the double-hoisting-point gate hoist according to the embodiment of the present invention when opening the gate;
in the figure: 11: a first hydraulic cylinder; 12: a second hydraulic cylinder; 21: a first hydraulic control check valve; 22: a second hydraulic control one-way valve; 3: a sequence valve; 41: a first electromagnetic directional valve; 42: a second electromagnetic directional valve; 43: a third electromagnetic directional valve; 44: a fourth electromagnetic directional valve; 45: a fifth electromagnetic directional valve; 52: a second shuttle valve; 53: a third shuttle valve; 61: a first cartridge valve; 62: a second cartridge valve; 63: a third cartridge valve; 64: a fourth cartridge valve; 65: a fifth cartridge valve; 71: a first overflow valve; 74: a fourth spill valve; 75: a fifth overflow valve; 81: a first safety overflow valve; 82, a second safety overflow valve; 91: a first oil pump; 92: a second oil pump; 10: a one-way valve.
Detailed Description
The following detailed description of the embodiments of the present invention is provided with reference to the accompanying drawings and examples. The following examples are intended to illustrate the invention, but are not intended to limit the scope of the invention.
The structure of a hydraulic system of a double-hoisting-point gate hoist in the prior art before improvement is shown in figure 1, and the starting and stopping control method comprises the following steps: when a gate needs to be opened, the two hydraulic pump motor sets are started in an idle state, about 10 seconds are delayed, the control valve sets DT1, DT3 and DT5 are electrified, the third cartridge valve 63 is opened by electrifying the DT3, hydraulic oil enters rod cavities of the two hydraulic cylinders through the third cartridge valve 63 and the hydraulic control one-way valve, piston rods of the hydraulic cylinders retract upwards, oil in a rodless cavity flows out, the DT4 is de-electrified, the fourth cartridge valve 64 is opened, and the oil in the rodless cavity flows back to an oil tank through the fourth cartridge valve 64; when a gate needs to be closed, a hydraulic pump motor set is started in an idle state, about 10 seconds are delayed, a control valve group DT1, DT2 and DT4 are electrified, a second cartridge valve 62 is opened due to the electrification of DT2, hydraulic oil is divided into two parts after passing through the second cartridge valve 62, one part of hydraulic oil enters control ports of a first hydraulic control one-way valve 21 and a second hydraulic control one-way valve 22, oil outlets of the first hydraulic control one-way valve 21 and the second hydraulic control one-way valve 22 are opened, DT5 loses the electricity, a fifth cartridge valve 65 is opened, DT4 is electrified, a fourth cartridge valve 64 is closed, rod cavity oil liquid of two hydraulic cylinders respectively enters a proportional speed regulating valve through the first hydraulic control one-way valve 21 and the second hydraulic control one-way valve 22 and then is combined into one part, the rod cavity liquid enters a rodless cavity for oil supplement after passing through the fifth cartridge valve 65, and the two hydraulic cylinders stretch out in a differential mode under the self-weight action of the gate; meanwhile, the other hydraulic oil enters the rodless cavities of the two hydraulic cylinders through the sequence valve 3 for oil supplement.
However, in the prior art, when the gate needs to be stopped in the process of closing the gate, DT2 is de-energized, the second cartridge valve 62 is closed, the control oil path between the second cartridge valve 62 and the control ports of the first hydraulic control one-way valve 21 and the second hydraulic control one-way valve 22 is closed, and the pressure of the control ports of the first hydraulic control one-way valve 21 and the second hydraulic control one-way valve 22 cannot be released, so that the first hydraulic control one-way valve 21 and the second hydraulic control one-way valve 22 cannot be closed in time, and the piston rods of the first hydraulic cylinder 11 and the second hydraulic cylinder 12 continue to extend out under the automatic action of the gate, which causes the phenomenon that the gate with double lifting points slides down, and affects the control accuracy of the gate opening and the operation safety of the gate.
In order to solve the problems, the application provides an improved hydraulic system of a double-hoisting-point gate hoist, as shown in fig. 2 to 4, the pilot oil path between the second cartridge valve 62 and the pilot ports of the first pilot check valve 21 and the second pilot check valve 22 is communicated with the second oil outlet port B of the second electromagnetic directional valve 42 in the pilot valve group DT2, when the operation of closing the gate is stopped, the hydraulic oil in the control ports of the first pilot-operated check valve 21 and the second pilot-operated check valve 22 can directly flow back to the oil tank through the port B of the second electromagnetic directional valve 42, the first pilot-operated check valve 21 and the second pilot-operated check valve 22 can be closed in time, therefore, the problem that the middle part cannot be stopped in time when the gate is closed and the gate continues to slide downwards is solved, the problem can be effectively solved when the gate is closed by the improved hydraulic system, and the opening of the gate by the improved hydraulic system can be smoothly carried out.
As shown in fig. 2-4, oil inlets of a first oil pump 91 and a second oil pump 92 connected with the electric motor are connected with an oil tank, oil outlets of the first cartridge valve 61, a second cartridge valve 62 and a third cartridge valve 63 are connected with oil inlets of the first cartridge valve 61, the second cartridge valve 62 and a fourth cartridge valve 64, oil outlets of the first cartridge valve 61 and the fourth cartridge valve 64 are connected with the oil tank through a return oil filter, an oil outlet of the second cartridge valve 62 is connected with an oil inlet of the sequence valve 3, a control port of the first hydraulic control one-way valve 21 and a control port of the second hydraulic control one-way valve 22, an oil outlet of the sequence valve 3 is connected with rodless cavities of the first hydraulic cylinder 11 and the second hydraulic cylinder 12, an oil drain port of the sequence valve 3 is connected with the oil tank, an oil outlet of the third cartridge valve 63 and an oil inlet of a fifth cartridge valve 65 are connected with oil inlets of the first hydraulic control one-way valve 21 and the second hydraulic control one-way valve 22, an oil outlet of the fifth cartridge valve 65 is connected with an oil inlet of the fourth cartridge valve 64, an oil outlet of the first one-way valve 21 is connected with a rod cavity of the first oil pump 11, the oil outlet of the second hydraulic control one-way valve 22 is connected with the rod cavity of the second oil pump 12; the oil drainage port of the first hydraulic control one-way valve 21 is connected with the rodless cavity of the first hydraulic cylinder, and the oil drainage port of the second hydraulic control one-way valve 22 is connected with the rodless cavity of the second hydraulic cylinder; an oil inlet of the one-way valve 10 is connected with an oil tank, and an oil outlet is connected with an oil outlet of the sequence valve 3; in order to protect the rod cavity, a first safety overflow valve 81 and a second safety overflow valve 82 are arranged, the oil inlet of the first safety overflow valve 81 is connected with the rod cavity of the first hydraulic cylinder 11, the oil outlet of the first safety overflow valve 81 is connected with the rodless cavity of the first hydraulic cylinder 11, the oil inlet of the second safety overflow valve 82 is connected with the rod cavity of the second hydraulic cylinder 12, and the oil outlet of the second safety overflow valve 82 is connected with the rodless cavity of the second hydraulic cylinder 12;
the control ports of the first cartridge valve 61, the fourth cartridge valve 64 and the fifth cartridge valve 65 are respectively connected with pressure control valve sets DT1, DT4 and DT5, the structures of the pressure control valve sets DT1, DT4 and DT5 are the same, the pressure control valve sets are used for controlling the closing and opening of the corresponding cartridge valves, the corresponding cartridge valves are closed when power is on, and the corresponding cartridge valves are opened when power is off; the pressure control valve group DT1 comprises a first electromagnetic directional valve 41 and a first overflow valve 71, wherein an oil inlet of the first electromagnetic directional valve 41 is a P port, an oil inlet of the first overflow valve 71 and a control port of the first cartridge valve 61 are connected with an oil inlet of the first cartridge valve 61 through damping holes, a second oil outlet of the first electromagnetic directional valve 41 is a B port, an oil return port is a T port and an oil outlet of the first overflow valve 71 are connected with an oil tank through an oil return filter; the pressure control valve group DT4 comprises a fourth electromagnetic directional valve 44 and a fourth overflow valve 74, an oil inlet of the fourth electromagnetic directional valve 44 is a port P, an oil inlet of the fourth overflow valve 74 and a control port of the fourth cartridge valve 64 are connected with an oil inlet of the fourth cartridge valve 64 through a damping hole, and a second oil outlet of the fourth electromagnetic directional valve 44 is a port B, an oil return port is a port T and an oil outlet of the fourth overflow valve 74 are connected with an oil tank; the pressure control valve group DT5 comprises a fifth electromagnetic directional valve 45 and a fifth overflow valve 75, wherein an oil inlet of the fifth electromagnetic directional valve 45 is a P port, an oil inlet of the fifth overflow valve 75 and a control port of the fifth cartridge valve 65 are connected with an oil inlet of the fifth cartridge valve 65 through a damping hole, a second oil outlet of the fifth electromagnetic directional valve 45 is a B port, an oil return port is a T port and an oil outlet of the fifth overflow valve 75 are connected with an oil tank; when the electromagnetic directional valve is in power failure, the port P is communicated with the port B, hydraulic oil returns to an oil tank through the port P and the port B, and no hydraulic oil acts on a control port of the cartridge valve, so that an oil inlet and an oil outlet of the cartridge valve are communicated when the electromagnetic directional valve is in power failure; when the electromagnetic directional valve is electrified, the port P is communicated with the port A, if the hydraulic oil pressure is higher than the set pressure of the overflow valve, the hydraulic oil returns to the oil tank through the overflow valve, and if the hydraulic oil is lower than the set pressure of the overflow valve, the hydraulic oil acts on the control port of the cartridge valve, so that the oil inlet and the oil outlet of the cartridge valve are not communicated when the electromagnetic directional valve is electrified, and the pressure of a controlled oil way is ensured not to exceed the set pressure of the overflow valve.
The control ports of the second cartridge valve 62 and the third cartridge valve 63 are respectively connected with directional control valve sets DT2 and DT3, the structures of the directional control valve sets DT2 and DT3 are the same, and the directional control valve sets are used for controlling the closing and opening of the corresponding cartridge valves, the corresponding cartridge valves are opened when power is supplied, and the corresponding cartridge valves are closed when power is lost; the direction control valve group DT3 comprises a third electromagnetic directional valve 43 and a third shuttle valve 53, wherein one oil inlet of the third shuttle valve 53 is connected with an oil inlet of the third cartridge valve 63, the other oil inlet of the third shuttle valve 53 is connected with an oil outlet of the second cartridge valve, the oil outlet is connected with an oil inlet (a port P) of the third electromagnetic directional valve 43 through a damping hole, an oil return port (a port T) of the third electromagnetic directional valve 43 is connected with an oil tank, and a first oil outlet (a port A) is connected with a control port of the third cartridge valve 63 through the damping hole; the direction control valve group DT2 comprises a second electromagnetic directional valve 42 and a second shuttle valve 52, wherein one oil inlet of the second shuttle valve 52 is connected with an oil inlet of the second cartridge valve 62, the other oil inlet of the second shuttle valve is connected with an oil outlet of the second cartridge valve, the oil outlet is connected with an oil inlet, namely a P port, of the second electromagnetic directional valve 42 through a damping hole, an oil return port, namely a T port, of the second electromagnetic directional valve 42 is connected with an oil tank, a first oil outlet, namely an A port, is connected with a control port of the second cartridge valve 62 through the damping hole, and a second oil outlet, namely a B port, is connected with an oil inlet of the sequence valve 3; when the electromagnetic directional valve is electrified, the port P is not communicated with the port A, hydraulic oil enables an oil inlet and an oil outlet of the shuttle valve to be communicated and enters the port P, no hydraulic oil flows out from the port A, and the control port of the cartridge valve has no hydraulic oil action, so that the oil inlet and the oil outlet of the cartridge valve are communicated when the electromagnetic directional valve is electrified; when the electromagnetic directional valve is powered off, the port P is communicated with the port A, hydraulic oil enables an oil inlet and an oil outlet of the shuttle valve to be communicated, enters the port P, flows out of the port A and acts on a control port of the cartridge valve, and therefore the oil inlet and the oil outlet of the cartridge valve are not communicated when the electromagnetic directional valve is powered off.
The first electromagnetic directional valve 41, the fourth electromagnetic directional valve 44 and the fifth electromagnetic directional valve 45 are two-position four-way electromagnetic directional valves, and the port P is communicated with the port B when power is off, the port T is communicated with the port A when power is on, and the port P is communicated with the port A and the port T is communicated with the port B when power is on; the second electromagnetic directional valve 42 and the third electromagnetic directional valve 43 are two-position four-way electromagnetic directional valves, and the port P is communicated with the port A, the port T is communicated with the port B when the power is off, and the port P is communicated with the port B and the port T is communicated with the port A when the power is on; the set pressure of the first overflow valve 71 is 22.5MPa, the set pressure of the fourth overflow valve 74 is 1.0MPa, and the set pressure of the fifth overflow valve 75 is 21.5 MPa; the set pressure of the first safety overflow valve 81 and the second safety overflow valve 82 is 22 MPa; the set pressure of the sequence valve 3 is 6 MPa.
In order to further prove that the improved hydraulic control system can not only effectively solve the problem of gliding when the gate is closed, but also ensure the normal operation of the opened gate, the operation processes of the closed gate and the opened gate of the hydraulic system are respectively explained, the improved hydraulic control system is only improved on the device, and the control mode is the same as that of the prior art before the improvement;
the two hydraulic cylinders are synchronized and identical in hydraulic control, and therefore, the first hydraulic cylinder 11 and the cylinder bypass valve group thereof inside and outside the station of the hydraulic system are used for explanation:
fig. 2 shows when the shutter is closed: when a hydraulic pump motor set is started in an idle state, about 10 seconds are delayed, DT1, DT2 and DT4 are electrified, DT3 and DT5 are electrified, so that the first cartridge valve 61 and the fourth cartridge valve 64 are closed, the second cartridge valve 62 is opened, the third cartridge valve 63 is closed, the fifth cartridge valve 65 is opened, the P port and the B port of the second electromagnetic directional valve 42 are communicated, the T port and the A port are communicated, hydraulic oil passes through the second cartridge valve 62 and then is divided into two streams, one stream of hydraulic oil enters the control ports of the first hydraulic control one-way valve 21 and the second hydraulic control one-way valve 22, the hydraulic oil entering the second shuttle valve 52 also enters the control ports of the first hydraulic control one-way valve 21 and the second hydraulic control one-way valve 22 through the P port and the B port of the second electromagnetic directional valve 42, so that the oil outlets of the first hydraulic control one-way valve 21 and the second hydraulic control one-way valve 22 are opened, the oil in the rod cavity of the first hydraulic cylinder 11 passes through the first hydraulic control one-way valve 21 and the proportional speed regulating valve, the oil liquid in the rod cavity of the second hydraulic cylinder 12 passes through the second hydraulic control one-way valve 22 and the proportional speed regulating valve, then is combined into one strand, passes through the fifth cartridge valve 65, and enters the rodless cavities of the first hydraulic cylinder 11 and the second hydraulic cylinder 12 along the oil way behind the oil outlet of the sequence valve 3 for oil supplement, and the two hydraulic cylinders extend out in a differential manner under the action of the dead weight of the gate; meanwhile, the other hydraulic oil enters the rodless cavities of the first hydraulic cylinder 11 and the second hydraulic cylinder 12 through the sequence valve 3 for oil supplement; if the oil in the rodless cavity is not enough, the oil can enter the rodless cavities of the first hydraulic cylinder 11 and the second hydraulic cylinder 12 along the oil way behind the oil outlet of the sequence valve 3 through the one-way valve for oil supplement, so that the hydraulic cylinders are prevented from generating a suction phenomenon;
fig. 3 shows that when the closing shutter operation is stopped: the DT1, DT2 and DT4 are de-energized, so that the first cartridge valve 61 and the fourth cartridge valve 64 are opened, the second cartridge valve 62 is closed, at the moment, the port P and the port A of the second electromagnetic directional valve 42 are communicated, the port T and the port B are communicated, the control oil between the second cartridge valve 62 and the control ports of the first pilot-operated check valve 21 and the second pilot-operated check valve 22 flows back to the oil tank through the port T through the port B of the second electromagnetic directional valve 42, the pressure of the control ports of the first pilot-operated check valve 21 and the first pilot-operated check valve 22 is released, and the pilot-operated check valves can be closed in time; therefore, the piston rods of the first hydraulic cylinder 11 and the second hydraulic cylinder 12 can be stopped in time, and the gate does not slide downwards any more;
fig. 4 shows the state when the shutter is opened: the two hydraulic pump motor sets are started in an idle state, about 10 seconds are delayed, DT1, DT3 and DT5 are electrified, DT2 and DT4 are electrified, so that the first cartridge valve 61 and the fifth cartridge valve 65 are closed, the third cartridge valve 63 is opened, the second cartridge valve 62 is closed, the fourth cartridge valve 64 is opened, hydraulic oil enters the rod cavities of the first hydraulic cylinder 11 and the second hydraulic cylinder 12 through the third cartridge valve 63, the proportional speed regulating valve, the first hydraulic control one-way valve 21 and the second hydraulic control one-way valve 22, the piston rods of the first hydraulic cylinder 11 and the second hydraulic cylinder 12 retract upwards, oil in the rod-free cavity flows out, and the hydraulic oil flows back to an oil tank through the fourth cartridge valve 64; therefore, opening the gate can be performed normally.
In summary, the improved hydraulic system of the double-hoisting-point gate hoist has the following advantages:
(1) the utility model discloses in time discharge the control oil of the control port of pilot operated check valve through the second oil-out of second electromagnetic directional valve, do not change the control mode among the prior art, but can effectively solve the gate and close the in-process and can't stop in time, namely the piston rod continues to stretch out downwards, causes the problem that two hoisting point gates glide, and gate closing and opening also can normally go on through hydraulic system;
(2) the pressure control valve group ensures that the pressure of the oil way does not exceed the set pressure of the overflow valve, and ensures the safe and stable operation of the hydraulic system; the rod cavity is also protected by a safety overflow valve;
(3) the utility model discloses a differential extension can be realized to hydraulic circuit for the piston rod fast action targets in place and the withdrawal, and can in time mend oil, prevents the emergence of suction phenomenon.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit it; although the embodiments of the present invention have been described in conjunction with the accompanying drawings, those skilled in the art may make various modifications and variations without departing from the spirit and scope of the invention, and such modifications and variations fall within the scope defined by the appended claims.
Claims (10)
1. An improved hydraulic system of a double-hoisting-point gate hoist is characterized by comprising an oil pump, a second cartridge valve and a second direction control valve set DT2 connected with the second cartridge valve, a third cartridge valve and a third direction control valve set DT3 connected with the third cartridge valve, a hydraulic cylinder and a cylinder side valve set of the hydraulic cylinder, and a sequence valve, the cylinder side valve group comprises a hydraulic control one-way valve, an oil inlet of the oil pump is connected with an oil tank, an oil outlet of the oil pump is connected with oil inlets of the second cartridge valve and the third cartridge valve, the oil outlet of the second cartridge valve is connected with the oil inlet of the sequence valve and the control port of the hydraulic control one-way valve, the oil outlet of the sequence valve is connected with the rodless cavity of the hydraulic cylinder, the oil drain port is connected with the oil tank, the oil outlet of the third cartridge valve is connected with the oil inlet of the hydraulic control one-way valve, an oil outlet of the hydraulic control one-way valve is connected with a rod cavity of the hydraulic cylinder, and an oil drainage port is connected with a rodless cavity of the hydraulic cylinder; DT2 includes second electromagnetic directional valve and second shuttle valve, an oil inlet of second shuttle valve is connected the oil inlet of second cartridge valve, another oil inlet is connected the oil-out of second cartridge valve, the oil-out is connected the oil inlet of second electromagnetic directional valve, the oil return opening of second electromagnetic directional valve connects the oil tank, first oil-out is connected the control port of second cartridge valve, the second oil-out is connected the oil inlet of sequence valve.
2. The improved hydraulic system of a double-hoisting-point gate hoist of claim 1, further comprising a first cartridge valve and a first pressure control valve group DT1 connected with the first cartridge valve, a fourth cartridge valve and a fourth pressure control valve group DT4 connected with the fourth cartridge valve, a fifth cartridge valve and a fifth pressure control valve group DT5 connected with the fifth cartridge valve, wherein an oil inlet of the first cartridge valve is connected with an oil outlet of the oil pump, oil outlets of the first cartridge valve and the fourth cartridge valve are connected with an oil tank, an oil inlet of the fourth cartridge valve is connected with an oil outlet of the fifth cartridge valve, and an oil inlet of the fifth cartridge valve is connected with an oil inlet of a hydraulic control one-way valve.
3. The improved hydraulic system of the double-hoisting-point gate hoist of claim 2, wherein the DT1 comprises a first electromagnetic directional valve and a first overflow valve, the oil inlet of the first electromagnetic directional valve, the oil inlet of the first overflow valve and the control port of the first cartridge valve are connected with the oil inlet of the first cartridge valve, and the oil return port of the first electromagnetic directional valve, the second oil outlet and the oil outlet of the first overflow valve are connected with an oil tank; the DT4 comprises a fourth electromagnetic directional valve and a fourth overflow valve, the DT5 comprises a fifth electromagnetic directional valve and a fifth overflow valve, and the connection relations among the electromagnetic directional valve, the overflow valve and the cartridge valve in the DT4 and the DT5 are the same as the connection relations among the electromagnetic directional valve, the overflow valve and the cartridge valve corresponding to the DT 1.
4. The improved hydraulic system of a double-hanging-point gate hoist according to claim 1, wherein the DT3 comprises a third electromagnetic directional valve and a third shuttle valve, an oil inlet of the third shuttle valve is connected with an oil inlet of the third cartridge valve, another oil inlet of the third shuttle valve is connected with an oil outlet of the third cartridge valve, an oil outlet of the third shuttle valve is connected with an oil inlet of the third electromagnetic directional valve, an oil return port of the third electromagnetic directional valve is connected with an oil tank, and a first oil outlet of the third shuttle valve is connected with a control port of the third cartridge valve.
5. The improved hydraulic system of a double-hanging-point gate hoist of claim 1, further comprising a check valve, wherein an oil inlet of the check valve is connected to an oil tank, and an oil outlet of the check valve is connected to an oil outlet of the sequence valve.
6. The improved dual drop gate hoist hydraulic system of claim 1, wherein the oil pump comprises a first oil pump and a second oil pump, the first oil pump and the second oil pump being connected to the motor, respectively.
7. The improved hydraulic system of a double-hanging-point gate hoist of claim 1, wherein the cylinder bypass valve set further comprises a safety overflow valve, an oil inlet of the safety overflow valve is connected with a rod cavity of the hydraulic cylinder, and an oil outlet of the safety overflow valve is connected with a rodless cavity of the hydraulic cylinder.
8. The improved hydraulic system of a double-lifting-point gate hoist of claim 1, wherein the hydraulic cylinders comprise a first hydraulic cylinder and a second hydraulic cylinder acting on two ends of the double-lifting-point gate, and an oil path at an oil outlet of the third cartridge valve is divided to connect a hydraulic control check valve in a cylinder side valve group of the first hydraulic cylinder and a hydraulic control check valve in a cylinder side valve group of the second hydraulic cylinder respectively.
9. The improved hydraulic system of a double-lifting-point gate hoist according to claim 3, characterized in that the set pressure of the first overflow valve is 22.5MPa, the set pressure of the fourth overflow valve is 1.0MPa, and the set pressure of the fifth overflow valve is 21.5 MPa; the first electromagnetic directional valve, the fourth electromagnetic directional valve and the fifth electromagnetic directional valve are communicated with the port P and the port B when the power is off, the port T is communicated with the port A, the port P is communicated with the port A when the power is on, and the port T is communicated with the port B.
10. The improved hydraulic system of a double-hoisting-point gate hoist according to claim 1, wherein the second electromagnetic directional valve and the third electromagnetic directional valve are communicated with the port P and the port A when the power is off, the port T is communicated with the port B, the port P is communicated with the port B when the power is on, and the port T is communicated with the port A; the set pressure of the sequence valve is 6 MPa.
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| CN202121202406.XU CN215171162U (en) | 2021-05-28 | 2021-05-28 | Improved hydraulic system of double-hoisting-point gate hoist |
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| CN202121202406.XU CN215171162U (en) | 2021-05-28 | 2021-05-28 | Improved hydraulic system of double-hoisting-point gate hoist |
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