CN212479739U - Closed hydraulic traveling brake valve set - Google Patents
Closed hydraulic traveling brake valve set Download PDFInfo
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- CN212479739U CN212479739U CN202020747298.3U CN202020747298U CN212479739U CN 212479739 U CN212479739 U CN 212479739U CN 202020747298 U CN202020747298 U CN 202020747298U CN 212479739 U CN212479739 U CN 212479739U
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Abstract
A closed hydraulic traveling brake valve group comprises a valve body, wherein an electro-hydraulic reversing valve and a plug-in overflow valve are arranged on the valve body, and two ends of a P port and a T port of the electro-hydraulic reversing valve are connected with the plug-in overflow valve; the sequence valve and the electromagnetic directional valve are further arranged on the valve body, the downstream of the sequence valve is connected with the electromagnetic directional valve, an oil outlet of the electromagnetic directional valve is respectively connected with the first check valve and the second check valve, a control oil port X3 of the sequence valve is connected with an inlet of the plug-in overflow valve, the upstream of the overflow valve is connected with an outlet of the sequence valve, and the downstream of the overflow valve is connected with a Y port on the valve body. The utility model provides a reverse brake force of valves can be adjusted according to the design parameter of difference, when running gear is dragged by turning over, can automatic detection backpressure and according to backpressure's size provide the certain control pressure oil of closed walking pump and make hydraulic system turn over the condition of dragging the engine and obtain alleviating, play the effect of protection engine and whole walking system.
Description
Technical Field
The utility model relates to a hydraulic control valve group, especially a reverse braking valves is used to capable actuating system of closed hydraulic pressure belongs to hydraulic control technical field.
Background
The large road maintenance machine as a railway engineering machine needs to have high-speed self-running capability, and the running drive of the current road maintenance machine vehicle comprises hydraulic drive, closed hydraulic drive, electric drive and the like. The hydraulic drive has the characteristics of compact structure and high power density, and the traveling speed of the hydraulic drive can reach 100km/h, so that the hydraulic drive is widely applied to large road maintenance machinery. The mechanism is simple, and basically the engine drives a closed oil pump which drives a hydraulic motor, and the hydraulic motor drives the running of the vehicle wheel pair. The closed hydraulic drive can realize stepless speed regulation, and the provided driving force is adaptive to the load resistance of the vehicle.
The objective of any drive mode is to achieve smooth running of the vehicle, and shock, overspeed, etc. are major factors that damage the hydraulic system. Because the dead weight of large-scale road maintaining machinery itself is all great, and inertia is big, and closed drive hydraulic system's rigidity is limited again, consequently when the system slows down suddenly, the vehicle is down big long ramp when appearing, the kinetic energy of vehicle can be absorbed by hydraulic system, when kinetic energy is big to hydraulic system can't absorb completely, can cause out of control of vehicle and cause the potential safety hazard. The path along which the kinetic energy of the vehicle is absorbed is: wheel set-hydraulic motor-enclosed oil pump-engine, when the kinetic energy absorbed by the vehicle is too large, the engine and system can be damaged. Therefore, a certain control device or method is required to avoid such problems.
Disclosure of Invention
In view of above-mentioned dangerous existence, the utility model provides a capable braking valves is walked to closed hydraulic pressure can restrict and walk the biggest reverse hydraulic braking pressure of capable actuating system to the size of the anti-power of holding back of effective control hydraulic pump to the engine guarantees that the engine and walks the component not impaired in the capable hydraulic circuit, makes the walking function of vehicle normally ensure the vehicle safe operation.
The technical scheme of the utility model is that: the electro-hydraulic reversing valve comprises a valve body, wherein an electro-hydraulic reversing valve and a plug-in overflow valve are arranged on the valve body, and two ends of a P port and a T port of the electro-hydraulic reversing valve are connected with the plug-in overflow valve; the sequence valve and the electromagnetic directional valve are further arranged on the valve body, the downstream of the sequence valve is connected with the electromagnetic directional valve, an oil outlet of the electromagnetic directional valve is respectively connected with the first check valve and the second check valve, a control oil port X3 of the sequence valve is connected with an inlet of the plug-in overflow valve, the upstream of the overflow valve is connected with an outlet of the sequence valve, and the downstream of the overflow valve is connected with a Y port on the valve body.
The port A and the port B of the electro-hydraulic reversing valve are connected with the valve body, and the port T, P of the electro-hydraulic reversing valve is connected with two ends of the plug-in type overflow valve.
The valve body is provided with ports A1 and A2 which are communicated with the port A, and ports B1 and B2 which are communicated with the port B.
The valve body is also provided with an X port for supplying oil to the electro-hydraulic reversing valve and the sequence valve, and the electro-hydraulic reversing valve controls the oil supply and the sequence valve to be supplied by the X port of the valve body.
And the valve body is also provided with Y ports for controlling oil drainage for the electro-hydraulic directional valve, oil drainage for the sequence valve, oil outlet of the overflow valve and oil return of the electromagnetic directional valve, and the electro-hydraulic directional valve controls the oil drainage for the electro-hydraulic directional valve, the oil drainage for the sequence valve, the oil outlet of the overflow valve and the oil return of the electromagnetic directional valve to be connected to the Y ports of the valve body.
The electro-hydraulic directional valve has H function, and the electromagnetic directional valve has Y function.
And a pressure measuring port M1 on the valve body is connected to the inlet of the plug-in overflow valve, and a pressure measuring port M2 on the valve body is connected to the inlet of the overflow valve.
The downstream of the check valve is output to an X1 port on the valve body, and the downstream of the check valve is output to an X2 port on the valve body.
Preferably, the main valve of the electro-hydraulic reversing valve is an H function four-position three-way reversing valve
Preferably, the pressure of the plug-in relief valve is set to 5 to 8 MPa.
Preferably, the sequence valve pressure is set to 12 MPa.
Preferably, the pressure of the relief valve is 4 MPa.
Preferably, the opening pressure of the first check valve and the second check valve is 0 MPa.
Preferably, the electromagnetic directional valve is a three-position four-way Y function directional valve.
Preferably, when the pressure of the sequence valve oil preparation port X3 reaches the set pressure of the sequence valve, the sequence valve is opened, and the pressure oil of the X port on the valve body can supply oil to the electromagnetic directional valve through the sequence valve.
The utility model discloses the reverse brake force of hydraulic pressure that produces in steerable large-scale mechanical equipment or the vehicle walking.
The utility model discloses well hydraulic pressure is walked line system and is can detect the change of walking pressure in the system drive circuit with reverse brake control valve, and automatic control walks the discharge capacity of pump, and restriction actuating system's the biggest reverse hydraulic braking force to the size of the anti-power of dragging of engine is walked to the line system of effective control, guarantees the normal function of engine and hydraulic drive return circuit component and the operational safety of whole car.
The utility model discloses the solenoid directional valve of installation in the valve body, overflow valve etc. adopt screw thread cartridge, compact structure, and reverse braking pressure control process is hydraulic pressure automatic control, and the reaction is rapid, sensitive, accurate, can effectively restrict to walk the biggest reverse hydraulic braking force of traveling system to the size of traveling system to the anti-power of dragging of engine is walked in the control, guarantees the normal function of engine and hydraulic drive return circuit component and the operational safety of whole car.
Drawings
Fig. 1 is a hydraulic schematic diagram of a preferred embodiment of a closed hydraulic traveling brake valve assembly according to the present invention;
FIG. 2 is a block diagram of the embodiment shown in FIG. 1;
FIG. 3 is a top view of the embodiment shown in FIG. 2;
FIG. 4 is a side view of the embodiment shown in FIG. 2;
FIG. 5 is a rear view of the embodiment of FIG. 2;
in the figure, an electro-hydraulic directional valve 3 of a valve body 1, an electro-hydraulic directional valve 3, an overflow valve 4, an electromagnetic directional valve 5, a one-way valve 6, a sequence valve 8 and the overflow valve are inserted.
Detailed Description
In fig. 1-5, the utility model discloses a valve body 1 sets up electricity liquid switching-over valve 2, cartridge overflow valve 3 and sequence valve 7 in this valve body 1, and cartridge overflow valve 3 is connected at the P, T mouths of electricity liquid switching-over valve 2, and electricity liquid switching-over valve 2's A, B mouth links to each other with A1, A2 and B1, B2 mouth on the valve body 1 respectively. The downstream of the sequence valve 7 is connected with an electromagnetic directional valve 4, the downstream of the electromagnetic directional valve 4 is connected with a one-way valve I5 and a one-way valve II 6, the downstream of the one-way valve I5 is output to an X1 port on the valve body 1, and the downstream of the one-way valve II 6 is output to an X2 port on the valve body 1. The upstream of the overflow valve 8 is connected with the outlet of the sequence valve 7, and the downstream of the overflow valve 8 is connected with the Y port on the valve body 1. The control oil of the sequence valve 7 and the control oil of the electro-hydraulic reversing valve 2 are supplied by an X port on the valve body 1, and the control oil drainage of the electro-hydraulic reversing valve 2, the drainage of the sequence valve 7 and the return oil of the electromagnetic reversing valve 4 are all connected to a Y port on the valve body 1. A pressure measuring port M1 on the valve body 1 is connected to an inlet of the plug-in type overflow valve 3, a pressure measuring port M2 on the valve body 1 is connected to an inlet of the overflow valve 8, the set pressure of the plug-in type overflow valve 3 is 5-8MPa, the pressure of the sequence valve 7 is set to be 12MPa, and the pressure of the overflow valve 8 is set to be 4 MPa.
The electro-hydraulic directional valve 2 includes a main valve and a pilot valve.
The main valve of the electro-hydraulic reversing valve comprises an A port, a B port, a P port and a T port.
The main valve of the electro-hydraulic reversing valve is an H function four-position three-way reversing valve.
The sequence valve is provided with a control port X3, and a control port X3 of the sequence valve 7 is connected to the inlet of the cartridge overflow valve 3
The opening pressure of the first check valve 5 and the second check valve 6 is 0 MPa.
The electromagnetic change valve 4 is a three-position four-way Y-function change valve.
When the pressure of the oil preparation port X3 of the sequence valve 7 reaches the set pressure of the sequence valve, the sequence valve 7 is opened, and the pressure oil of the port X on the valve body 1 can supply oil to the electromagnetic directional valve 4 through the sequence valve 7.
The utility model discloses a theory of operation is:
working condition 1: travelling forwards
When the walking control handle is operated forwards, the vehicle moves forwards, and assuming that the port A1 of the closed walking pump is high pressure and the port B1 is low pressure at the moment, the electromagnet at the end a of the pilot valve of the electro-hydraulic reversing valve is electrified, the pilot valve works at the left position, the oil from the port X of the valve body flows to the left end of the main valve through the pilot valve, so that the main valve is at the left working position, and the high-pressure oil of the walking system flows through the port A1 on the valve body 1 → the port A of the main valve of the electro-hydraulic reversing valve → the port P of the main valve of the electro-hydraulic. According to the working principle of the plug-in overflow valve, the method comprises the following steps: at this time, the plug-in relief valve 3 is in a closed state, and high-pressure oil passes through a port a2 in the valve body to reach the travel motor. When the vehicle runs on a downhill road section, the motor becomes a pump working condition due to inertia acceleration or deceleration by pulling back the traveling handle in the normal traveling process, the high-pressure side of the traveling loop becomes a low-pressure side, and the low-pressure side becomes a high-pressure side. The pressure at the port B1 (original low pressure side) of the closed-type running pump is increased, and the oil flow direction is as follows: the port B2 on the valve body → the port B of the main valve of the electro-hydraulic reversing valve → the port T of the main valve of the electro-hydraulic reversing valve → the oil inlet of the plug-in type overflow valve 3, the larger the ramp or the faster the handle is pulled back, the faster the pressure of the port B1 of the walking drive pump rises, and the motor becomes the working condition of the pump, so that the walking system generates reverse hydraulic braking force. When the pressure of the port B reaches the set pressure of the sequence valve 7, the pressure oil passes through the port B of the main valve of the electro-hydraulic directional control valve → the main valve T of the electro-hydraulic directional control valve → the port X3 of the sequence valve, the sequence valve 7 is opened, the oil of the port X on the valve body 1 passes through the sequence valve 7 → the electro-magnetic directional control valve 4 → the check valve 5 → the closed pump control port X1, when the pressure oil of the port X exceeds the set value of the relief valve 8, the pressure oil overflows from the relief valve 8, and the pressure oil entering the electro-magnetic directional control valve 4 is stabilized below the set pressure value of the relief valve 8, the pressure of the port X1 is increased, so that the displacement of the walking pump is increased, the rotating speed of an oil pump is reduced, the oil pump is rigidly connected with the engine, and the anti-dragging rotating speed of the engine is also reduced to an allowable range, so that the engine and hydraulic elements of a circuit are protected from being damaged.
Working condition 2: backward self-running:
when the walking handle is pushed backwards to walk, assuming that the port B1 of the walking driving pump is on the high-pressure side at the moment, a microswitch or a walking direction selection switch on the walking handle sends a signal to enable an electromagnet at the B end of a pilot valve of the electro-hydraulic reversing valve 2 to be electrified, the right position (cross position) of the electro-hydraulic reversing valve 2 works, control oil reaches the right position (cross position) of a main valve of the electro-hydraulic reversing valve 2 to work, and high-pressure oil flows out from an oil inlet of the plug-in type overflow valve 3 through the port B → the T port → the main valve of the electro-hydraulic reversing valve 2 at the moment. According to the working principle of the overflow valve, the following steps are known: the overflow valve is in a closed state at this time.
When the vehicle runs on a downhill road section, the motor becomes a pump working condition due to inertia acceleration or deceleration by pulling back the traveling handle in the normal traveling process, the high-pressure side of the traveling loop becomes a low-pressure side, and the low-pressure side becomes a high-pressure side. The pressure at port A1 (original low pressure side) of the closed-type running pump is increased, and the oil flow direction is as follows: the port A2 on the valve body → the port A of the main valve of the electro-hydraulic reversing valve 2 → the port T of the main valve of the electro-hydraulic reversing valve 2 → the oil inlet of the plug-in type overflow valve 3, the larger the ramp or the faster the handle is pulled back, the faster the pressure of the port A1 of the walking driving pump rises, and the motor becomes the pump working condition, so that the walking system generates reverse hydraulic braking force. When the pressure of the port B reaches the pressure of the sequence valve 7, the pressure oil passes through the port B of the main valve of the electro-hydraulic reversing valve → the main valve T of the electro-hydraulic reversing valve → the port X3 of the sequence valve, the sequence valve 7 is opened, and the oil flow of the port X on the valve body 1 is as follows: when the pressure oil at the port X exceeds the set value of the plug-in overflow valve 8, the pressure oil overflows from the plug-in overflow valve 8, so that the pressure oil entering the electromagnetic directional valve 4 is stabilized below the set pressure value of the plug-in overflow valve 8, the pressure at the port X2 is increased, the displacement of the traveling pump is increased, the rotating speed of the oil pump is reduced, the oil pump is rigidly connected with the engine, and the anti-dragging rotating speed of the engine is also reduced within an allowable range, so that the engine and hydraulic elements of a circuit are protected from being damaged.
Claims (8)
1. The utility model provides a closed hydraulic pressure is walked to line brake valve group which characterized in that: the hydraulic reversing valve comprises a valve body (1), wherein an electro-hydraulic reversing valve (2) and a plug-in overflow valve (3) are arranged on the valve body (1), and two ends of a P port and a T port of the electro-hydraulic reversing valve (2) are connected with the plug-in overflow valve (3); the sequence valve (7) and the electromagnetic directional valve (4) are further arranged on the valve body (1), the downstream of the sequence valve (7) is connected with the electromagnetic directional valve (4), an oil outlet of the electromagnetic directional valve (4) is respectively connected with a one-way valve I (5) and a one-way valve II (6), a control oil port X3 of the sequence valve (7) is connected with an inlet of the plug-in overflow valve (3), the upstream of the overflow valve (8) is connected with an outlet of the sequence valve (7), and the downstream of the overflow valve (8) is connected with a Y port of the valve body (1).
2. The closed hydraulic service brake block of claim 1, wherein: the port A and the port B of the electro-hydraulic reversing valve (2) are connected with the valve body (1), and the port T, P of the electro-hydraulic reversing valve (2) is connected with the two ends of the plug-in overflow valve (3).
3. The closed hydraulic service brake block of claim 2, wherein: the valve body (1) is provided with ports A1 and A2 which are communicated with the port A, and ports B1 and B2 which are communicated with the port B.
4. The closed hydraulic service brake block of claim 1, wherein: an X port for supplying oil to the electro-hydraulic reversing valve (2) and the sequence valve (7) is further arranged on the valve body (1).
5. The closed hydraulic service brake block of claim 1, wherein: the valve body (1) is also provided with a Y port for controlling oil drainage of the electro-hydraulic directional valve (2), oil drainage of the sequence valve (7), oil outlet of the overflow valve (8) and oil return of the electromagnetic directional valve (4).
6. The closed hydraulic service brake block of claim 1, wherein: the electro-hydraulic directional valve (2) has H function, and the electromagnetic directional valve (4) has Y function.
7. The closed hydraulic service brake block of claim 1, wherein: and a pressure measuring port M1 on the valve body (1) is connected to the inlet of the plug-in overflow valve (3), and a pressure measuring port M2 on the valve body (1) is connected to the inlet of the overflow valve (8).
8. The closed hydraulic service brake block of claim 1, wherein: the downstream of the one-way valve I (5) is output to an X1 port on the valve body (1), and the downstream of the two-way valve (6) is output to an X2 port on the valve body (1).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020747298.3U CN212479739U (en) | 2020-05-09 | 2020-05-09 | Closed hydraulic traveling brake valve set |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020747298.3U CN212479739U (en) | 2020-05-09 | 2020-05-09 | Closed hydraulic traveling brake valve set |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN212479739U true CN212479739U (en) | 2021-02-05 |
Family
ID=74459412
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202020747298.3U Active CN212479739U (en) | 2020-05-09 | 2020-05-09 | Closed hydraulic traveling brake valve set |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN212479739U (en) |
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2020
- 2020-05-09 CN CN202020747298.3U patent/CN212479739U/en active Active
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CB03 | Change of inventor or designer information |
Inventor after: Yang Houchang Inventor after: Xing Lei Inventor after: Fang Lizhi Inventor after: Li Kang Inventor after: Wang Chengzhe Inventor after: Liu Xin Inventor after: Dong Bangxiong Inventor after: Fang Renjie Inventor before: Yang Houchang Inventor before: Xing Lei Inventor before: Fang Lizhi Inventor before: Li Kang Inventor before: Wang Chengzhe Inventor before: Liu Xin Inventor before: Dong Bangxiong Inventor before: Fang Renjie |
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| CB03 | Change of inventor or designer information |