CN109899333A - Valve block, hydraulic control system and vehicle - Google Patents
Valve block, hydraulic control system and vehicle Download PDFInfo
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- CN109899333A CN109899333A CN201910248288.7A CN201910248288A CN109899333A CN 109899333 A CN109899333 A CN 109899333A CN 201910248288 A CN201910248288 A CN 201910248288A CN 109899333 A CN109899333 A CN 109899333A
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- restricting element
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Abstract
The invention discloses a kind of valve block, hydraulic control system and vehicles, belong to technical field of hydraulic.Valve block of the present invention includes oil inlet P, first throttle element, second restricting element, first reversal valve and the second reversal valve, oil inlet P with slippage pump driven by the engine for being connected to, the import of first throttle element and the second restricting element is connected to oil inlet P, the outlet of first reversal valve and the second reversal valve is connected to the both ends of the variable cylinder for pilot plunger pump swash plate angle respectively, the import of first reversal valve is configured as the outlet with first throttle element in the first state, in the second condition with the outlet of the second restricting element, the import of second reversal valve is configured as the outlet with the second restricting element in the first state, in the second condition with the outlet of first throttle element.Valve block and hydraulic control system of the present invention are able to achieve engine speed and pumpage relevant control, and structure is simple, can use with the controller combination of other hydraulic controls.
Description
Technical field
The present invention relates to technical field of hydraulic more particularly to a kind of valve blocks, hydraulic control system and vehicle.
Background technique
CA control is automatic control mode relevant to engine speed, the control pressure that built-in CA control pressure circuit generates
Power is proportional to engine speed, can be applied to vehicle to run system.The forward or backward direction of vehicle is by switch electromagnet control
System, CA control pressure and by switch electromagnet enter main pump variable control system, and ratio of the main pump on two-way may be implemented and arrange
Amount control.I.e. engine speed is higher, then discharge of main pump is bigger.Meanwhile CA controls the anti-stall control of Built-in mechanical engine
Circuit, when system, which absorbs power, reaches setting value, the meeting backswing of main pump swash plate reduces flow system flow, to prevent engine from occurring
Carry phenomenon.CA control mode can the variable displacement motor with quantitative, variable, high-voltage feedback motor or with pressure feedback form system,
Modularized design enables the system to realize multiple functions and control mode.
But existing CA controller is placed outside on plunger pump, can only realize the ratio of simple engine and pumpage
Example control, can not be applied in combination with other fluid controllers, and the scope of application is limited.
Summary of the invention
It can be realized engine speed and pumpage relevant control an object of the present invention is to provide one kind and be applicable in
The wide valve block of range, hydraulic control system and vehicle.
For this purpose, on the one hand, the invention adopts the following technical scheme:
A kind of valve block, comprising:
Oil inlet P is used to be connected to slippage pump driven by the engine；
First throttle element, import are connected to the oil inlet P；
Second restricting element, import are connected to the oil inlet P, and outlet pressure is lower than the first throttle element
Outlet pressure；
First reversal valve is exported for being connected to the first end for variable cylinder, and the variable cylinder is used for pilot plunger
The swash plate angle of pump, the import of first reversal valve are configured as connecting with the outlet of first throttle element in the first state
The logical, outlet with the second restricting element in the second condition；And
Second reversal valve is exported for being connected to the second end of the variable cylinder, the import quilt of second reversal valve
It is configured to connect with the outlet of the second restricting element, in the second condition with the outlet of first throttle element in the first state
It is logical.
In one embodiment, the valve block further include: third restricting element, import are connected to the oil inlet P,
Outlet is connected to for the repairing mouth with plunger pump.
In one embodiment, the outlet of the import of second restricting element and the third restricting element.
In one embodiment, further include be set to it is unidirectional between first reversal valve and second reversal valve
Valve, the check valve are configured such that fluid can only flow to first reversal valve from second reversal valve.
In one embodiment, it is arranged between the outlet of the first throttle element and the import of second restricting element
There is the first overflow valve.
It in one embodiment, further include the second overflow valve being connected to the oil inlet P.
In one embodiment, the first throttle element and/or second restricting element are what throttle diameter can be changed
Restricting element.
In one embodiment, the third restricting element is the restricting element that throttle diameter can be changed.
In one embodiment, first reversal valve and second reversal valve are two-position three-way valve.
In one embodiment, the valve block is vehicle valve block.
On the other hand, the invention adopts the following technical scheme:
A kind of hydraulic control system, including engine, slippage pump, plunger pump and valve block described in any of the above embodiments.
In another aspect, the invention adopts the following technical scheme:
A kind of vehicle, including above-mentioned hydraulic control system.
Beneficial effects of the present invention are as follows:
Valve block, hydraulic control system and vehicle provided by the invention, when engine speed improves, slippage pump The hydraulic oil
Greatly, become larger from the flow of the high-voltage end of reversal valve entering variable cylinder, so that the movement of variable cylinder becomes larger, so as to cause plunger pump row
Amount increases；Conversely, plunger pumpage reduces when engine speed is slow, engine speed relationship proportional to pumpage is realized,
Realize engine speed and pumpage relevant control；And plunger pump is realized by the commutation of the first reversal valve and the second reversal valve
The control of fuel feeding forward or backwards, and then realize the control of vehicle traveling direction；Meanwhile this valve block structure is simple, it is at low cost, and
It can be applied in combination with other hydraulic controllers, realize the combination of multiple functions and control mode, improve the control performance to pump,
The scope of application is wider.
Detailed description of the invention
Fig. 1 is the structural schematic diagram for the hydraulic control system that the specific embodiment of the invention provides；
Fig. 2 is the structural schematic diagram for the variable cylinder that the specific embodiment of the invention provides；
Fig. 3 is the structural schematic diagram when valve block that the specific embodiment of the invention provides is in first state；
Fig. 4 is the structural schematic diagram when valve block that the specific embodiment of the invention provides is in the second state.
Appended drawing reference:
100, slippage pump；200, valve block；300, plunger pump；400, variable cylinder；
210, first throttle element；220, the second restricting element；230, third restricting element；240, the first reversal valve；
250, the second reversal valve；260, check valve；270, the first overflow valve；280, the second overflow valve；410, cylinder body；420, piston；
430, elastic component；411, the first end of variable cylinder；412, the second end of variable cylinder.
Specific embodiment
To further illustrate the technical scheme of the present invention below with reference to the accompanying drawings and specific embodiments.
In the description of the present invention, it is to be understood that, term " on ", "lower", "front", "rear", "left", "right", " perpendicular
Directly ", the orientation or positional relationship of the instructions such as "horizontal", "top", "bottom", "inner", "outside" is orientation based on the figure or position
Relationship is set, is merely for convenience of description of the present invention and simplification of the description, rather than the device or element of indication or suggestion meaning are necessary
It with specific orientation, is constructed and operated in a specific orientation, therefore is not considered as limiting the invention.
A specific embodiment of the invention provides a kind of hydraulic control system and the vehicle using the hydraulic control system,
To realize engine speed and pumpage relevant control.As shown in Figure 1, the hydraulic control system includes that engine (does not show in figure
Out), slippage pump 100, valve block 200, plunger pump 300 and variable cylinder 400.100 pump oil of engine driving slippage pump, variable cylinder 400
For the swash plate angle of pilot plunger pump 300, slippage pump 100 is adjusted by valve block 200 come the output of regulated variable cylinder 400
The discharge capacity of plunger pump 300.
Optionally, as shown in Fig. 2, variable cylinder 400 includes cylinder body 410 and the piston 420 being set in cylinder body 410, variable
The both ends (i.e. the first end 411 of variable cylinder and the second end 412 of variable cylinder) of cylinder 400 are respectively arranged with two with piston 420
The hydraulic oil port of end face connection, piston 420 are directly or indirectly connect with swash plate.Optionally, the two sides of piston 420 and cylinder body
Elastic component 430 is provided between 410, the elastic force that the elastic component of 420 two sides of piston is provided to piston 420 is preferably equal.Valve
Block 200 is for the position of the piston 420 of regulated variable cylinder 400 and then the angle of adjusting swash plate.Wherein, cylinder body 410 can with but not
It is limited as including two cylinder units, the both ends of piston 420 seal respectively to be matched in two cylinder units, two cylinder units
On be respectively arranged with the hydraulic oil port being connected to two end faces of piston 420.
As shown in Figure 3 and Figure 4, valve block 200 includes oil inlet P, first throttle element 210, the second restricting element 220, the
Three restricting elements 230, the first reversal valve 240 and the second reversal valve 250.Oil inlet P with slippage pump 100 for being connected to, first segment
The import of fluid element 210, the second restricting element 220 and third restricting element 230 is connected to oil inlet P, third restricting element
230 outlet be connected to the repairing mouth of plunger pump 300 using plunger pump 300 have hydraulic oil leakage when as plunger pump 300
Repairing (trend of the slave third restricting element 230 that the arrow in the downstream F indicates in Fig. 1 to oil liquid between 300 repairing mouth of plunger pump), the
The outlet pressure of two restricting elements 220 is lower than the outlet pressure of the first throttle element 210.Wherein, third restricting element 230
Between the repairing mouth of plunger pump 300 can with but be not limited to be provided with third overflow valve.The outlet A of first reversal valve 240 with
The first end 411 of variable cylinder 400 is connected to, and the outlet B of the second reversal valve 250 is connected to the second end 412 of variable cylinder 400.Valve block
200 include first state and the second state, under first state, the import of the first reversal valve 240 and going out for first throttle element 210
Mouth connection, the outlet of the import of the second reversal valve 250 and the second restricting element 220, so that the first end of variable cylinder 400
411 pressure is greater than the pressure of the second end 412 of variable cylinder 400, and the positive fuel feeding of plunger pump 300, is driven by plunger pump 300 at this time
Motor rotate forward, i.e., motor to make vehicle advance direction rotate；Under second state, the import of the first reversal valve 240 with
The outlet of second restricting element 220, the import of the second reversal valve 250 and the outlet of first throttle element 210, so that
The pressure of the second end 412 of variable cylinder 400 is greater than the pressure of the first end 411 of variable cylinder 400, and plunger pump 300 reversely supplies at this time
Oil is rotated backward by the motor that plunger pump 300 drives, i.e. motor is to rotating the direction of vehicle rollback.
Wherein, the first reversal valve 240 and the second reversal valve 250 preferably but are not limited to two position three way directional control valve.Specifically
Ground, two imports of the first reversal valve 240 are respectively the first import and the second import, and the import of the second reversal valve 250 is respectively
Third import and the 4th import.Under first state, the outlet of the first import and first throttle element 210, third import with
The outlet of second restricting element 220；Under second state, the outlet of the 4th import and first throttle element 210, second
The outlet of import and the second restricting element 220.
The valve block 200 that present embodiment provides, when engine speed improves, 100 The hydraulic oil of slippage pump is big, from
The flow of the high-voltage end of reversal valve entering variable cylinder 400 becomes larger, so that the movement of variable cylinder 400 becomes larger, and then influences swash plate
Tilt angle causes 300 discharge capacity of plunger pump to increase；Conversely, 300 discharge capacity of plunger pump reduces when engine speed is slow, hair is realized
Motivation revolving speed relationship proportional to pumpage realizes engine speed and pumpage relevant control；And pass through the first reversal valve
240 and second the commutation of reversal valve 250 realize the control of the fuel feeding forward or backwards of plunger pump 300, and then realize vehicle traveling side
To control；Meanwhile this 200 structure of valve block is simple, it is at low cost, and can be applied in combination with other hydraulic controllers, it realizes a variety of
The combination of function and control mode, improves the control performance to pump, and the scope of application is wider.
As shown in Figure 3 and Figure 4, the outlet of the import of the second restricting element 220 and third restricting element 230, a side
Face is less than the outlet pressure of first throttle element 210 by the outlet pressure that throttling twice is easily achieved the second restricting element 220,
On the other hand the structure of valve block 200 is simplified.It should be noted that the second restricting element can also be enabled in other embodiments
220 import is directly connected to oil inlet P, can guarantee that the outlet pressure of the second restricting element 220 is less than first throttle element 210
Outlet pressure.
For the ease of adjust first throttle element 210 outlet and the second restricting element 220 exit pressure, first
At least one of restricting element 210, the second restricting element 220 and third restricting element 230 are the throttling that throttle diameter can be changed
Element.Such as it can be at least one of first throttle element 210, the second restricting element 220 and third restricting element 230
Moveable baffle is set at throttle orifice, the area that baffle blocks throttle orifice is adjusted by the position of mobile baffle, and then adjust
Save throttle diameter.It is of course also possible to the restricting element for selecting other existing throttle diameters variable.
If the first end 411 of pipeline rupture at the outlet A of the first reversal valve 240, variable cylinder 400 loses oil pressure, and becomes
412 normal fuel injection of second end for measuring cylinder 400, will lead to the reversed fuel feeding of plunger pump 300.At this point, using the vehicle of hydraulic control system
It can be travelled backward suddenly from normally travel, extremely dangerous, to solve this problem, valve block 200 further includes being set to first to change
Check valve 260 between valve 240 and the second reversal valve 250, check valve 260 are configured such that fluid can only be from the second commutation
Valve 250 flows to the first reversal valve 240.If pipeline rupture at the outlet A of the first reversal valve 240, check valve 260 is opened, will be former
This is guided from the part oil liquid that the second throttle orifice flows to the second reversal valve 250 into the first reversal valve 240, ensure that the first commutation
The pressure value in 250 exit of valve 240 and the second reversal valve is equal, that is, keeps the pressure value at 400 both ends of variable cylinder equal, at this time
The swash plate angle of plunger pump 300 is essentially a zero, plunger pump 300 do not have variable, vehicle will stop motion, to ensure that driving
Safety.
When engine power is big, 100 revolving speed of slippage pump is high, the outlet of first throttle element 210 and the second restricting element
Pressure difference between 220 outlet is big, and the pressure difference of 400 two sides of variable cylinder is big, and then causes the discharge capacity of plunger pump 300 high.For control
Discharge capacity is provided with the first overflow valve 270 between the outlet of first throttle element 210 and the import of the second restricting element 220, when
When pressure difference between the outlet of first throttle element 210 and the import of the second restricting element 220 is higher than preset value, the first overflow valve
270 open, and part oil liquid flows to the second restricting element 220 from first throttle element 210, drops the pressure difference of 400 two sides of variable cylinder
It is low, and then guarantee that the discharge capacity of plunger pump 300 is unlikely to excessive.
Under the low temperature environments such as winter, hydraulic oil viscosity is big when vehicle launch, may cause hypertonia at restricting element,
Influence the safety of whole system.To solve this problem, optionally, valve block 200 further includes that second be connected to oil inlet P is overflow
Valve 280 is flowed, when system pressure is excessively high, the second overflow valve 280 is opened in oil liquid overflow to oil return box or other containers, makes system
Pressure no longer increase to avoid pressure overload, protection system.
The course of work of the hydraulic control system of present embodiment offer is briefly provided below in conjunction with Fig. 1 to Fig. 4:
When vehicle normally advances when driving, as shown in Figure 1 to Figure 3, the first reversal valve 240 is powered, and the second reversal valve 250 is disconnected
Electricity, the outlet of the first import and first throttle element 210, the outlet of third import and the second restricting element 220, i.e.,
Valve block 200 is in first state.The oil liquid of 200 oil inlet P of valve block is divided into two-way, all the way through first throttle element 210 and first
Enter the first end 411 of variable cylinder 400 after the outlet A of reversal valve 240；Another way enters third restricting element 230, third throttling
The oil liquid that element 230 flows out is divided into two-way again, enters plunger pump 300 when plunger pump 300 has hydraulic oil leakage all the way
Repairing mouth, the second end of outlet B entering variable cylinder 400 of the another way through the second restricting element 220 and the second reversal valve 250
412, since the big pressure in 210 exit of first throttle element is greater than the pressure in 220 exit of the second restricting element, variable cylinder 400
The oil pressure of first end 411 is greater than the oil pressure of the second end 412 of variable cylinder 400, the positive fuel feeding of plunger pump 300, so that motor
Drive vehicle forward.Furthermore, it is possible to adjust vehicle by the revolving speed for controlling engine come the discharge capacity of pilot plunger pump 300
The speed of service.
When vehicle rollback, as shown in figure 4, the first reversal valve 240 power off, the second reversal valve 250 be powered, the 4th import with
The outlet of first throttle element 210, the outlet of the second import and the second restricting element 220, i.e. valve block 200 are in the
Two-state.The oil liquid of 200 oil inlet P of valve block is divided into two-way, all the way going out through first throttle element 210 and the second reversal valve 250
Enter the second end 412 of variable cylinder 400 after mouth B；Another way enters third restricting element 230, what third restricting element 230 flowed out
Oil liquid is divided into two-way again, has the repairing mouth for entering plunger pump 300 when hydraulic oil leakage in plunger pump 300 all the way,
The first end 411 of outlet A entering variable cylinder 400 of the another way through the second restricting element 220 and the first reversal valve 240, due to the
The big pressure in one restricting element, 210 exit is greater than the pressure in 220 exit of the second restricting element, 400 second end 412 of variable cylinder
Oil pressure is greater than the oil pressure of its first end 411, the reversed fuel feeding of plunger pump 300, so that motor drives vehicle rollback.Moreover, can
The speed of service of vehicle is adjusted come the discharge capacity of pilot plunger pump 300 by the revolving speed for controlling engine.
The technical principle of the invention is described above in combination with a specific embodiment.These descriptions are intended merely to explain of the invention
Principle, and shall not be construed in any way as a limitation of the scope of protection of the invention.Based on the explanation herein, the technology of this field
Personnel can associate with other specific embodiments of the invention without creative labor, these modes are fallen within
Within protection scope of the present invention.
Claims (10)
1. a kind of valve block characterized by comprising
Oil inlet P is used to be connected to slippage pump driven by the engine (100)；
First throttle element (210), import are connected to the oil inlet P；
Second restricting element (220), import are connected to the oil inlet P, and outlet pressure is lower than the first throttle element
(210) outlet pressure；
First reversal valve (240), outlet A with the first end (411) of variable cylinder (400) for being connected to, the variable cylinder (400)
For pilot plunger pump (300) swash plate angle, the import of first reversal valve (240) be configured as in the first state with
The outlet of first throttle element (210), the in the second condition outlet with the second restricting element (220)；And
Second reversal valve (250), for being connected to the second end (412) of the variable cylinder (400), described second changes outlet B
To the import of valve (250) be configured as in the first state with the outlet of the second restricting element (220), in the second condition
With the outlet of first throttle element (210).
2. valve block according to claim 1, which is characterized in that the valve block further include:
Third restricting element (230), import are connected to the oil inlet P, are exported for the benefit with the plunger pump (300)
Hydraulic fluid port connection.
3. valve block according to claim 2, which is characterized in that the import of second restricting element (220) and described the
The outlet of three restricting elements (230).
4. valve block according to any one of claims 1 to 3, which is characterized in that further include being set to first reversal valve
(240) check valve (260) between second reversal valve (250), the check valve (260) are configured such that fluid only
First reversal valve (240) can be flowed to from second reversal valve (250).
5. valve block according to any one of claims 1 to 3, which is characterized in that the outlet of the first throttle element (210)
The first overflow valve (270) are provided between the import of second restricting element (220).
6. valve block according to any one of claims 1 to 3, which is characterized in that further include be connected to the oil inlet P
Two overflow valves (280).
7. valve block according to claim 2 or 3, which is characterized in that the first throttle element (210), second section
Fluid element (220) and/or the third restricting element (230) are the restricting element that throttle diameter can be changed.
8. valve block according to any one of claims 1 to 3, which is characterized in that first reversal valve (240) and described
Two reversal valves (250) are two-position three-way valve.
9. a kind of hydraulic control system, which is characterized in that including engine, slippage pump (100), plunger pump (300) and such as right
It is required that 1 to 8 described in any item valve blocks (200).
10. a kind of vehicle, which is characterized in that including hydraulic control system as claimed in claim 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910248288.7A CN109899333B (en) | 2019-03-29 | 2019-03-29 | Valve block, hydraulic control system and vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910248288.7A CN109899333B (en) | 2019-03-29 | 2019-03-29 | Valve block, hydraulic control system and vehicle |
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| Publication Number | Publication Date |
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| CN109899333A true CN109899333A (en) | 2019-06-18 |
| CN109899333B CN109899333B (en) | 2020-06-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910248288.7A Active CN109899333B (en) | 2019-03-29 | 2019-03-29 | Valve block, hydraulic control system and vehicle |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112727814A (en) * | 2020-12-28 | 2021-04-30 | 浙江大学 | Variable-speed and variable-displacement single-rod electro-hydraulic actuator |
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| CN206830550U (en) * | 2017-03-07 | 2018-01-02 | 佛山市科达液压机械有限公司 | The open type pump that can reversely export |
| CN107906064A (en) * | 2017-12-25 | 2018-04-13 | 邵阳维克液压股份有限公司 | The device and variable method for control speed of changeable constant pressure variable displacement pump variable speed |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3854847A (en) * | 1972-02-22 | 1974-12-17 | Putzmeister Interholding Gmbh | Apparatus for damping the pressure increase of hydrostatic drives |
| CN2116797U (en) * | 1992-03-21 | 1992-09-23 | 建设部长沙建筑机械研究所 | Closed oil-way hydraulic control device |
| CN102275223A (en) * | 2011-09-20 | 2011-12-14 | 四川大学 | Novel rotation driving system for mixing drum of concrete mixing transport vehicle |
| CN203684314U (en) * | 2013-12-30 | 2014-07-02 | 华侨大学 | Load-sensitive excavator negative flow system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112727814A (en) * | 2020-12-28 | 2021-04-30 | 浙江大学 | Variable-speed and variable-displacement single-rod electro-hydraulic actuator |
| CN112727814B (en) * | 2020-12-28 | 2022-06-28 | 浙江大学 | Variable-speed and variable-displacement single-rod electro-hydraulic actuator |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109899333B (en) | 2020-06-02 |
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