CN106762928A - Automobile hydraulic system and the engineering truck with it - Google Patents
Automobile hydraulic system and the engineering truck with it Download PDFInfo
- Publication number
- CN106762928A CN106762928A CN201710029806.7A CN201710029806A CN106762928A CN 106762928 A CN106762928 A CN 106762928A CN 201710029806 A CN201710029806 A CN 201710029806A CN 106762928 A CN106762928 A CN 106762928A
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- Prior art keywords
- valve
- reversal valve
- outlet
- reversal
- import
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Power Steering Mechanism (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The present invention relates to automobile hydraulic system, engineering truck.Automobile hydraulic system includes：First pump and the second pump, by the engine driving of vehicle；Steering control valve, including the first reversal valve, the second reversal valve and pressure-control valve, steering control valve has first state and the second state, in first state, the import of the first reversal valve is turned on the first outlet of the first reversal valve, the import of the second reversal valve is turned on the second reversal valve first outlet, so that the first pump and the second pump provide hydraulic fluid to steering；In the second state, the import of the first reversal valve is both turned on the first reversal valve first outlet and second outlet, so that the pressure of the hydraulic fluid that the first outlet of pressure-control valve the first reversal valve of control is exported to steering.The technical scheme of the application is applied, power steering less problem when improving excessively sensitive steering wheel when high engine speeds present in prior art are rotated, low engine speed rotation.
Description
Technical field
The present invention relates to engineering machinery field, in particular to a kind of automobile hydraulic system and the engineering truck with it
.
Background technology
Widely, its multiple fields for having served national economy, its hydraulic system includes for loader-digger application
Steering boost system and equipment system.Steering boost system is generally using the machinery that reliability is higher, manufacturing cost is relatively low
Hydraulic booster, mechanical-hydraulic power-assisted is divided into gerotor type and permanent current formula according to action mode.Due to constant pressure hydraulic force aid system
Fluid in pipeline is always to maintain high pressure conditions so that the service life of hydraulic booster system is not high, so loader-digger is all
Using the mechanical-hydraulic force aid system of permanent current formula.
But current constant flow hydraulic force aid system haves the shortcomings that intrinsic, constant flow hydraulic force aid system uses constant displacement pump,
When loader-digger speed is very fast, because engine speed is higher, the fluid flow of pump output is larger, causes steering wheel " hair
Float ", the sensation to driver is lighter, and the power of steering wheel rotation seems too small, is unfavorable for vehicle carry out side of the driver to fast running
To control.When loader-digger travel speed is relatively low, because engine speed is relatively low, constant displacement pump output fluid flow compared with
Small, hydraulic steering cylinder stretches out speed slowly, and the effect of power steering is poor, and steering wheel relatively sinks to the sensation of driver, and driver turns to
Arduously.
The content of the invention
The present invention is intended to provide a kind of automobile hydraulic system and the engineering truck with it, exist in the prior art to improve
High engine speeds power steering less problem when steering wheel is excessively sensitive, low engine speed is rotated when rotating.
One side according to embodiments of the present invention, the invention provides a kind of automobile hydraulic system, including：
First pump and the second pump, by the engine driving of vehicle；
Steering control valve, including the first reversal valve, the second reversal valve and pressure-control valve, the first reversal valve have import,
First outlet and second outlet, the first reversal valve can be connected with the first pump, and the first outlet of the first reversal valve is used to connect car
Steering, the second outlet of the first reversal valve connects with pressure-control valve, and the second reversal valve has import, first outlet
And second outlet, the import of the second reversal valve can connect with the second pump, and the first outlet of the second reversal valve is used to connect vehicle
Steering, the second outlet of the second reversal valve is used to connect fluid tank,
Steering control valve has first state and the second state,
In first state, the import of the first reversal valve is turned on the first outlet of the first reversal valve, and the second reversal valve enters
Mouth and the conducting of the second reversal valve first outlet, so that the first pump and the second pump provide hydraulic fluid to steering；
In the second state, the import of the first reversal valve is both turned on the first reversal valve first outlet and second outlet, so that
The pressure of the hydraulic fluid that the first outlet of pressure-control valve the first reversal valve of control is exported to steering.
Alternatively, pressure-control valve includes counterbalance valve.
Alternatively, the first reversal valve also has control fluid intake, and control fluid intake is used to introduce the output of the first pump
Hydraulic fluid, causes that the import of the first reversal valve and the first reversal valve first go out with when the pressure of hydraulic fluid is higher than predetermined value
Mouth and second outlet are both turned on.
Alternatively, the first reversal valve includes the first proportional reversing valve, and the first reversal valve includes the first valve element, the first valve element tool
There are first position and make the first outlet and second of the first reversal valve that the first outlet for only making the first reversal valve is turned on import
Outlet with import turn on the second place, the first valve element at first position, the first outlet output hydraulic pressure of the first reversal valve
Pressure of the pressure of fluid less than the hydraulic fluid that the first reversal valve import is introduced.
Alternatively, the first reversal valve also includes the first chamber of the first end for being arranged on the first valve element and is arranged on the first valve
The inlet communication of the second chamber at the second end of core, first chamber and the first reversal valve, to introduce the first valve element to first
The hydraulic fluid of pushing is put, second chamber is connected with the first outlet of the first reversal valve, to introduce the first valve element to second
Put the hydraulic fluid of pushing.
Alternatively, the second reversal valve also includes the first elastomeric element, and the first elastomeric element is arranged in second chamber.
Alternatively, the second reversal valve also includes control fluid intake, and control fluid intake is used to introduce the output of the first pump
Hydraulic fluid, to cause that the import of the second reversal valve is turned on first outlet when the pressure of hydraulic fluid is less than predetermined value.
Alternatively, the second reversal valve includes the second valve element, the 3rd chamber of the first end for being arranged on the second valve element and setting
In the 4th chamber at the second end of the second valve element, the second valve element has makes the of the import of the second reversal valve and first outlet conducting
One position and make the second place of import and second outlet conducting, the 3rd chamber is turned on the first outlet of the first reversal valve, with
The hydraulic fluid that introducing pushes the second valve element to its second place, the import conducting of the 4th chamber and the second reversal valve, to draw
Enter the hydraulic fluid that the second valve element is pushed to the first position of the second valve element.
Alternatively, the second reversal valve also includes the second elastomeric element, and the second elastomeric element is arranged in the 3rd chamber.
Alternatively, the second reversal valve includes the second proportional reversing valve.
According to the another aspect of the application, a kind of engineering truck, including above-mentioned automobile hydraulic system are additionally provided.
Using the technical scheme of the application, when low engine speed is run, steering control valve is in first state, first
The first outlet conducting of state, the import of the first reversal valve and the first reversal valve, the import of the second reversal valve and the second reversal valve
First outlet is turned on, so that the first pump and the second pump provide hydraulic fluid to steering, therefore is improved in the prior art
Power steering less problem when the low engine speed of presence is rotated.When high engine speeds are run, steering control valve is in the
Two-state, in the second state, the import of the first reversal valve is both turned on the first reversal valve first outlet and second outlet, so that pressure
The pressure of the hydraulic fluid that the first outlet of force control valve the first reversal valve of control is exported to steering.Therefore improve existing
Steering wheel excessively sensitive issue when high engine speeds present in technology are rotated, advantageously accounts for side present in prior art
To the problem that disk is unstable.
By referring to the drawings to the detailed description of exemplary embodiment of the invention, further feature of the invention and its
Advantage will be made apparent from.
Brief description of the drawings
In order to illustrate more clearly about the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing
The accompanying drawing to be used needed for having technology description is briefly described, it should be apparent that, drawings in the following description are only this
Some embodiments of invention, for those of ordinary skill in the art, without having to pay creative labor, may be used also
Other accompanying drawings are obtained with according to these accompanying drawings.
Fig. 1 shows the automobile hydraulic system structural representation of embodiments of the invention；
Fig. 2 shows the partial schematic diagram of the automobile hydraulic system of embodiments of the invention；
Fig. 3 shows the schematic diagram of the steering control valve of the automobile hydraulic system of embodiments of the invention；
Fig. 4 shows the front view of the steering control valve of the automobile hydraulic system of embodiments of the invention；
Fig. 5 shows the left view of the steering control valve of the automobile hydraulic system of embodiments of the invention；
Fig. 6 shows the generalized section at A-A in Fig. 5；
Fig. 7 shows the right view of the steering control valve of the automobile hydraulic system of embodiments of the invention；
Fig. 8 shows the generalized section at B-B in Fig. 7；
Fig. 9 shows the top view of the steering control valve of the automobile hydraulic system of embodiments of the invention；
Figure 10 shows the upward view of the steering control valve of the automobile hydraulic system of embodiments of the invention；And
Figure 11 shows the rearview of the steering control valve of the automobile hydraulic system of embodiments of the invention.
In figure：100th, power part；200th, steering；300th, work system；400th, the first performs device；30th, control is turned to
Valve processed；40th, turning gradient control valve；50th, valve is excavated；60th, valve is loaded；70th, 2/2-way solenoid directional control valve；1st, engine；2nd, first
Reversal valve；3rd, engine；4th, the first pump；5th, the second pump；6th, filter；7th, fluid tank；8th, overflow valve；9th, the second reversal valve；10、
First check valve；11st, the second check valve；12nd, steering cylinder；13rd, flux amplification valve；14th, steering gear；15th, Stress control
Valve；16th, fluid circuit；21st, the 3rd locating part；22nd, the first taper valve core；23rd, the 3rd elastomeric element；24th, valve body；25th, first
Locating part；26th, the first valve element；27th, the first elastomeric element；28th, the second locating part；29th, the second valve element；210th, the second elastic portion
Part；211st, the 4th elastomeric element；212nd, the second taper valve core.
Specific embodiment
Below in conjunction with the accompanying drawing in the embodiment of the present invention, the technical scheme in the embodiment of the present invention is carried out clear, complete
Site preparation is described, it is clear that described embodiment is only a part of embodiment of the invention, rather than whole embodiments.Below
Description only actually at least one exemplary embodiment is illustrative, and never conduct is to the present invention and its application or makes
Any limitation.Based on the embodiment in the present invention, those of ordinary skill in the art are not making creative work premise
Lower obtained every other embodiment, belongs to the scope of protection of the invention.
Fig. 1 shows the structural representation of the automobile hydraulic system of the present embodiment, and Fig. 2 shows the office of automobile hydraulic system
Portion's schematic diagram, Fig. 3 shows the structural representation of the steering control valve of the present embodiment.The automobile hydraulic system of the present embodiment is digging
Dig the hydraulic system of loading machine.
With reference to shown in Fig. 1 and Fig. 2, automobile hydraulic system includes power part 100, and power part 100 includes the first pump 4 and second
Pump 5, the first pump 4 and the first pump 5 drive by the engine 3 of vehicle.The import of the first pump 4 and the second pump 5 connects with fluid tank 4
It is logical.
Automobile hydraulic system also includes turning gradient control valve 40, and turning gradient control valve 40 includes that import, first outlet and second go out
Mouthful.Turning gradient control valve 40 has first state and the second state, in first state, the import of turning gradient control valve 40 and first outlet
Conducting.In the second state, the first outlet and second outlet of turning gradient control valve 40 are turned on import.
Automobile hydraulic system also includes steering 200, the steering control valve 30 for controlling Vehicular turn and job family
System 300.Loader-digger includes excavation portion and loading part, and excavation portion includes scraper bowl, and loading part includes loader(-mounted) shovel.
Work system 300 is included for driving the first performs device 400 of dipper motion, for controlling the first performs device
Excavation valve 50, for drive loader(-mounted) shovel act the second performs device and for control the second performs device loading valve 60.
Loading valve 60 includes import, first outlet and second outlet.The import for loading valve 60 goes out with the first of pressure-gradient control valve 40
Mouth is connected by fluid circuit 16, loads the first outlet of valve 60 and the inlet communication of 2/2-way solenoid directional control valve 70, two
The outlet of two electric change valves 70 and fluid tank.Load the second outlet and the inlet communication for excavating valve 50 of valve 60.
Steering control valve 30 includes the first reversal valve 2, the second reversal valve 9 and pressure-control valve 15, and the first reversal valve 2 has
Import, first outlet and second outlet, the import of the first reversal valve 2 can be connected with the first pump 4, and the first of the first reversal valve 2
The steering for connecting vehicle is exported, the second outlet of the first reversal valve 2 is connected with pressure-control valve 15, the second reversal valve
9 have import, first outlet and second outlet, and the import of the second reversal valve 9 can be connected with the second pump 5, the second reversal valve 9
First outlet is used to connect the steering of vehicle, and the second outlet of the second reversal valve 9 is used to connect fluid tank 7.
Steering control valve 30 also includes safety valve 1, the import of safety valve 1 and the inlet communication of the first reversal valve 2, installs valve
2 outlet is connected with the first outlet of the first reversal valve 2.
Steering control valve 30 has first state and the second state.In 3 low cruise of engine, at steering control valve 30
In first state, in first state, the import of the first reversal valve 2 is turned on the first outlet of the first reversal valve 2, the second reversal valve
9 import is turned on the first outlet of the second reversal valve 9, so that the first pump 4 and the second pump 5 provide flow of pressurized to steering
Body, therefore improve power steering less problem when low engine speed present in prior art is rotated.
In 3 high-speed cruising of engine, steering control valve 30 is in the second state, in the second state, the first reversal valve 2
Import is both turned on the first outlet of the first reversal valve 2 and second outlet, so that pressure-control valve 15 controls the of the first reversal valve 2
One pressure for exporting the hydraulic fluid exported to steering.Therefore high engine speeds present in prior art are improved to rotate
When steering wheel excessively sensitive issue, advantageously account for the unstable problem of steering wheel present in prior art.
Automobile hydraulic system also includes the filter 6 being arranged between the second outlet of the second reversal valve 9 and fluid tank 7,
Filter 6 flows to the hydraulic fluid of fluid tank 7 for filtering the second outlet of the second reversal valve 9.
Automobile hydraulic system also includes the outlet of overflow valve 8, the import of overflow valve 8 and the second pump 5, overflow valve 8
Outlet and fluid tank, the pressure of the hydraulic fluid to control the import of the second reversal valve 9 introduced.
Automobile hydraulic system also includes the first check valve 10, the import of the first check valve 10 and the first of the second reversal valve 9
Outlet, outlet and the inlet communication of steering 200 of the first check valve 10.
Automobile hydraulic system also includes the second check valve 11, the import of the second check valve 11 and the first of the first reversal valve 2
Outlet, outlet and the inlet communication of steering 200 of the second check valve 11.
In the present embodiment, pressure-control valve 15 includes counterbalance valve.When steering control valve 30 is in the second state, counterbalance valve energy
The Stress control of enough hydraulic fluids that the first outlet of the first reversal valve 2 is exported to steering 200 is in predetermined value, so as to turn
Tend to constant to power-assisted.
First reversal valve 2 also has control fluid intake, and control fluid intake is used to introduce the flow of pressurized of the output of the first pump 4
Body, with cause when the pressure of hydraulic fluid is higher than predetermined value the import of the first reversal valve 2 and the first outlet of the first reversal valve 2 and
Second outlet is both turned on, so that pressure-control valve 15 controls the hydraulic pressure that the first outlet of the first reversal valve 2 is exported to steering
The pressure of fluid.
Fig. 4 shows the front view of the steering control valve 30 of the present embodiment, and Fig. 5 shows the left view of steering control valve,
Fig. 6 shows the sectional view at the A-A of steering control valve 30.
With reference to shown in Fig. 4 to 6, first reversal valve 2 of the present embodiment includes the first proportional reversing valve, and the first reversal valve 2 is wrapped
The first valve element 26 is included, the first valve element 26 is with the first position for only making the first outlet of the first reversal valve 2 be turned on import and makes
The first outlet and second outlet of the first reversal valve 2 with import turn on the second place, the first valve element 26 at first position,
Pressure of the pressure of the first outlet output hydraulic pressure fluid of the first reversal valve 2 less than the hydraulic fluid that the import of the first reversal valve 2 is introduced
Power.
First reversal valve 2 also includes the first elastomeric element 27 for the first valve element 26 to be urged to first position.First
Elastomeric element 27 is arranged in second chamber.Alternatively, the first elastomeric element 27 includes spring.
First reversal valve 2 also includes the first chamber of the first end for being arranged on the first valve element 26 and is arranged on the first valve element 26
The second end second chamber, the inlet communication of first chamber and the first reversal valve 2, to introduce the first valve element 26 to second
Put the hydraulic fluid of pushing.Second chamber is connected with the first outlet of the first reversal valve 2, to introduce the first valve element 26 to first
The hydraulic fluid that position pushes.
As shown in fig. 6, steering control valve 30 includes valve body 24, the first hole is provided with valve body 24.First valve element 26 is set
Can move in the first hole and along the first hole.The first end of the first valve element 26 forms first chamber, the second of the first valve element 26
End forms second chamber.
The first end of the first valve element 26 is additionally provided with the first locating part 25, and through hole is provided with the first locating part 25, so that
Hydraulic fluid in first chamber can act on the first end with the first valve element 26.
The hydraulic fluid of the output of the first pump 4 is delivered in the import and first chamber of the first reversal valve 2, the first reversal valve 2
First outlet output hydraulic fluid be delivered in second chamber.
When low engine speed is run, the hydraulic fluid of the import introducing of the first reversal valve 2 and the first of the first reversal valve 2
The pressure difference for exporting the hydraulic fluid of output is smaller, therefore the first valve element 26 is maintained at first in the presence of the first elastomeric element 27
Position.
When high engine speeds are run, the hydraulic fluid of the import introducing of the first reversal valve 2 and the first of the first reversal valve 2
The pressure difference for exporting the hydraulic fluid of output is larger, therefore the first valve element 26 is moved to second chamber, with the second place.
Second reversal valve 9 also includes control fluid intake, and control fluid intake is used to introduce the flow of pressurized of the output of the first pump 4
Body, to cause that the import of the second reversal valve 2 is turned on first outlet when the pressure of hydraulic fluid is less than predetermined value.
Second reversal valve 9 is including the second valve element 29, the 3rd chamber of the first end for being arranged on the second valve element 29 and is arranged on
4th chamber at the second end of the second valve element 29, the second valve element 29 has makes the import of the second reversal valve 9 and first outlet conducting
First position and make the second place of import and second outlet conducting.
Second reversal valve 9 also includes the second elastomeric element 210 for the second valve element 29 to be pushed to first position, second
Elastomeric element 210 is arranged in the 3rd chamber.Alternatively, the second elastomeric element 27 includes spring.
The inlet communication of the 3rd chamber and the first reversal valve 2, to introduce the second valve element 29 is pushed to its second place
Hydraulic fluid, the 4th chamber is connected with the first outlet of the second reversal valve 2, to introduce the second valve element 29 to the of the second valve element
The hydraulic fluid that one position pushes.
The second hole is provided with the valve body 24 of steering control valve 30, the second valve element 29 is arranged in the second hole and being capable of edge
Move in the second hole.The first end of the second valve element 29 forms the 3rd chamber, and the second end of the second valve element 29 forms the 4th chamber.
Second end of the second valve element 29 is additionally provided with the second locating part 28, and through hole is provided with the second locating part 28, so that
Hydraulic fluid in 3rd chamber can act on the first end with the second valve element 29.
Alternatively, the second reversal valve 9 includes the second proportional reversing valve.
When low engine speed is run, the hydraulic fluid of the import introducing of the first reversal valve 2 and the first of the first reversal valve 2
The pressure difference for exporting the hydraulic fluid of output is smaller, therefore the first valve element 26 is maintained at first in the presence of the first elastomeric element 27
Position, the second valve element 29 is maintained at first position under the use of the second elastomeric element 210, so that steering control valve 30 is in first
State.
When high engine speeds are run, the hydraulic fluid of the import introducing of the first reversal valve 2 and the first of the first reversal valve 2
Export output hydraulic fluid pressure difference it is larger, therefore the first valve element 26 to second chamber movement with the second place；Second
Valve element 29 to the 4th chamber movement with the second place so that steering control valve 30 is in the second state.
It is shown in Figure 6, it is additionally provided with the 3rd hole on the valve body 24 of steering control valve 30, pressure-control valve 15 is included by the
The 3rd elastomeric element 23, the first taper valve core 22 and the 3rd locating part 21 that the bottom in three holes sets gradually.3rd locating part 21
The side back to the first taper valve core 22 communicated with the import of pressure-control valve 15, the first taper valve core 22 back to the 3rd limit
The side of position part 21 communicates with the outlet of pressure-control valve 15.
First-class body opening is provided with 3rd locating part 21, the core of the first cone valve 22 coordinates to change stream with first-class body opening
Amount.
As shown in figure 8, being additionally provided with the 4th hole on the valve body 24 of steering control valve 30, safety valve 1 is included by the 4th hole
The 4th elastomeric element 211, the second taper valve core 212 and the 4th locating part 213 that bottom sets gradually.
The side back to the second taper valve core 212 of the 4th locating part 213 communicates with the import of safety valve 1, the second taper
The side back to the 4th locating part 213 of valve element 212 communicates with the outlet of safety valve 1.
With reference to shown in Fig. 4 to 11, hydraulic fluid port a, hydraulic fluid port b, oil are provided with the valve body 24 of the steering control valve 30 of the present embodiment
Mouth c, hydraulic fluid port d, hydraulic fluid port e, hydraulic fluid port f and hydraulic fluid port g.
Steering control valve 30 includes the first reversal valve 2, the first reversal valve 9, pressure-control valve 15, safety valve 1.Wherein pressure
The control port of valve 15 is controlled to be connected with hydraulic fluid port a, the oil-out of pressure-control valve 15 is connected with hydraulic fluid port g.
The import of safety valve 1, the import of the first reversal valve 2, the 4th chamber of the second reversal valve 9 are connected with hydraulic fluid port f, peace
The outlet of full valve 1, the first outlet of the first reversal valve 2, the 3rd chamber of the second reversal valve 9 are connected with b mouthfuls.
The import of the second reversal valve 9 is connected with hydraulic fluid port d, and the first outlet of the second reversal valve 9 is connected with hydraulic fluid port c；Second changes
Connected with hydraulic fluid port e to the second outlet of valve 9.
Fig. 4 shows the front view of the steering control valve 30 of the present embodiment.As shown in figure 4, before steering control valve 30
Upper setting hydraulic fluid port a, fabrication hole h, fabrication hole i, fabrication hole j, fabrication hole k, fabrication hole l and fabrication hole m.
Fig. 5 shows the left view of the steering control valve 30 of the present embodiment, as shown in figure 5, on the left side of steering control valve
It is provided with fabrication hole n, fabrication hole o and fabrication hole p.
Fig. 7 shows the right view of the steering control valve 30 of the present embodiment, as shown in fig. 7, the course changing control of the present embodiment
Fabrication hole q, fabrication hole r, fabrication hole s and fabrication hole t are provided with the right side of valve 30.
Fig. 9 shows the top view of the steering control valve 30 of the present embodiment.As shown in figure 9, the top surface of steering control valve 30
From setting gradually hydraulic fluid port b, hydraulic fluid port c, hydraulic fluid port d, fabrication hole u and fabrication hole v.
Figure 10 shows the upward view of the steering control valve 30 of the present embodiment.As shown in Figure 10, the bottom of steering control valve 30
Hydraulic fluid port f, hydraulic fluid port e, fabrication hole w, fabrication hole x are from left to right set gradually on face.
Figure 11 shows the rearview of the steering control valve 30 of the present embodiment.As shown in figure 11, after steering control valve 30
Hydraulic fluid port g is set on face.
Fabrication hole u on the top surface of steering control valve 30 drills through the fabrication hole o to the left side, the work on fabrication hole v and the right side
Skill hole q, the fabrication hole i for above going up are drilled through.
The left side is drilled with three fabrication holes, from fabrication hole n and the 3rd hole, the top surface fabrication hole for forming pressure-control valve 15
U is drilled through, and fabrication hole o is drilled through with fabrication hole u, the fabrication hole x on bottom surface on top surface, fabrication hole w on fabrication hole p and bottom surface,
Fabrication hole x and hydraulic fluid port f are drilled through.
The right side is drilled with four fabrication holes, fabrication hole v on fabrication hole q and the fabrication hole l, top surface that above go up, above goes up
Fabrication hole h is drilled through, and fabrication hole r and fabrication hole m, is led to for forming the 4th hole drill of internal security valve；Fabrication hole s and hydraulic fluid port d, oil
Mouth c is drilled through, and fabrication hole t and hydraulic fluid port d, hydraulic fluid port e are drilled through.
Referring to shown in Fig. 4,6 and 10, bottom surface is drilled with two fabrication holes, and fabrication hole p on fabrication hole w and the left side, first are changed
Drilled through to the first chamber of valve 2, fabrication hole x is drilled through with fabrication hole o, the fabrication hole p on the left side.
Above be drilled with six fabrication holes, fabrication hole h is drilled through with fabrication hole q, the hydraulic fluid port b on the right side, fabrication hole j be used for shape
Drilled through into the 4th hole of safety valve, hydraulic fluid port b, fabrication hole k leads to for forming the 4th hole drill of safety valve；Fabrication hole i and top surface
On fabrication hole v, the spring terminal of the first reversal valve 2 drills through；Right side from top to bottom first fabrication hole l and right side left side on to
Lower first fabrication hole q, the 3rd chamber of the second reversal valve 9 are drilled through, fabrication hole r, the second reversal valve on fabrication hole m and the right side
9 the 4th chambers are drilled through.
The automobile hydraulic system of the present embodiment is the hydraulic system of loader-digger, in the course of work of loader-digger
In:
When loader-digger is turned to, the hydraulic fluid that the first pump 4 is provided is delivered to by turning gradient control valve 40 and turns
To system 200.
The loader-digger steering procedure of the present embodiment has two states：One is middle steering of running at high speed, and two is low speed row
Sail middle steering.
Run at high speed in steering procedure, the hydraulic fluid for flowing into steering 200 enters steering control valve 30.Above-mentioned liquid
What pressure fluid was first passed around is the first proportional reversing valve 2, and the first proportional reversing valve 2 is originally under spring force in the right side
Position, due to having throttling action when the first reversal valve 2 is in right position, therefore the import of the first reversal valve 2 and first outlet it
Between can produce certain pressure difference.
When loader-digger is run at high speed, the rotating speed of engine 3 is higher, and the flow by the first reversal valve 2 is larger, because
This produce chock pressure difference it is also larger because the inlet pressure of the first reversal valve 2 act on the first reversal valve 2 without spring terminal,
The pressure of the first outlet of the first reversal valve 2 acts on the spring terminal of the first reversal valve 2.
When the spring terminal of the first reversal valve 2 and the pressure difference without spring terminal be more than spring force when, the first reversal valve 2 can gradually to
Left position transformation.It is proportioning valve due to using the first reversal valve 2, by right position, position changes the first reversal valve 2 to the left, until passing through
First reversal valve 2 enter steering flow caused by the first reversal valve 2 import and first outlet between pressure difference with
Untill spring dynamic balance.And unnecessary hydraulic fluid is transported to by the passage and pressure-control valve 15 of the left position of the first reversal valve 2
Fluid tank 7.
By the hydraulic fluid of the first reversal valve 2, on the one hand diverted device 14 acts on flux amplification valve 13, so that flow
Amplifying valve 13 commutates, and the flux amplification valve 13 on the other hand being turned on after check valve 11 and commutation enters steering cylinder 12,
To realize power steering, i.e., enter the hydraulic fluid flow rate of power-assisted oil cylinder by flux amplification valve when loader-digger is run at high speed
It is fixed, the power-assisted oil cylinder time of stretching out is also fixed, and the spring force only with the first reversal valve 2 is relevant, not by its dependent variable
Influence, the spring force that power-assisted oil cylinder stretches out time and the first reversal valve 2 has following relation：
Wherein, t stretches out the time for power-assisted oil cylinder；It is power-assisted oil cylinder piston active area；L power-assisted oil cylinder piston strokes；S is
First proportional reversing valve core active area；K is the orifice shapes coefficient of the first proportional reversing valve, is first proportional reversing valve mouthful etc.
Effect orifice size；F is the spring force of the first reversal valve 2.
The spring force of the first reversal valve 2 is slightly smaller than due to the spring force of the second reversal valve 9, so under the second reversal valve 9
Position enters system, and the hydraulic fluid of the output of the second pump 5 passes through the direct fluid tank 7 of filter 6.
In loader-digger runs at a low speed steering procedure, the hydraulic fluid for flowing into steering 200 is still to enter first
Enter the first reversal valve 2 in steering control valve 30, when being run at a low speed due to loader-digger, engine speed is relatively low, by
The flow of one reversal valve 2 is smaller, thus the first reversal valve 2 import and first outlet between pressure difference it is also smaller, if the pressure difference
It is not enough to overcome the spring force of the first reversal valve 2, the first reversal valve 2 can keep right position access system work under spring force
Make.Now because the differential pressure action of the import of the first reversal valve 2 and first outlet is not enough in the upper and lower ends of the second reversal valve 9 again
Overcome spring force, thus the second reversal valve upper access system, the hydraulic fluid of the output of the second pump 5 is by check valve 10 and logical
The hydraulic fluid interflow of the first reversal valve 2 and check valve 11 is crossed, the Flow amplification that the hydraulic fluid behind interflow passes through the conducting that commutates
Valve 13 enters steering cylinder 12, realizes power steering.The movement of actual engine speed and steering control valve proportional valve spool
There is following relation position：
When running at high speed, (Q11>Or=Q) when, Δ L=L；
When running at a low speed, (Q11<When Q),
Wherein, Δ L be steering control valve in second change valve 2 valve element 26 displacement variable；L is the second proportional reversing valve
Core displacement stroke；Q11It is the rate of discharge of check valve 11；Q is the first proportional reversing valve spring set flow in steering control valve；K
It is the orifice shapes coefficient of the valve element of the first reversal valve 2；A is the equivalent orifice size of the first proportional reversing valve mouthful, and F is the first ratio
Commutation valve spring force；N is whole machine actual engine speed；Q is quantitative pumpage；S is the first proportional reversing valve core active area；
∝ is the second proportional reversing valve inflow-rate of water turbine and its open area fraction coefficient, e be the second proportional reversing valve core aperture area and its
The proportionality coefficient of displacement.
When loader-digger is not turned to, hydraulic pump 4 provide flow by turning gradient control valve 40 controlling stream
To work system 300, loader-digger does not carry out steering and is directed to two states：One is overall operation, equipment action；
Two is whole machine straight-line travelling or idling parking.
When overall operation, equipment are acted, 2/2-way solenoid directional control valve 70 is powered, and electromagnet overcomes the spring force to make two
The position upper access system of two electric change valve 70, the hydraulic oil for flowing into work system 200 initially enters loading valve 60, Ran Houyou
To load valve 60 and export in 2/2-way solenoid directional control valve 70 and be cut off with the path of fluid tank, hydraulic oil will enter and excavate valve 50 and carry out
Operation.When whole machine straight-line travelling or idling parking, 2/2-way solenoid directional control valve 70 is in off-position, and spring force makes two
The next access system of position two electric change valve 70, flows into the hydraulic oil of work system 200 after loading valve 60, directly from
2/2-way solenoid directional control valve 70 returns to fluid tank 7.It is to be noted that under both the above state, the stream of the output of the second pump 5
Amount flows back to fluid tank 7 through overflow valve 8.
Exemplary embodiment of the invention is the foregoing is only, is not intended to limit the invention, it is all in spirit of the invention
Within principle, any modification, equivalent substitution and improvements made etc. should be included within the scope of the present invention.
Claims (11)
1. a kind of automobile hydraulic system, it is characterised in that including：
First pump (4) and the second pump (5), drive by the engine (3) of vehicle；
Steering control valve (30), including the first reversal valve (2), the second reversal valve (9) and pressure-control valve (15), described first changes
To valve (2) with import, first outlet and second outlet, first reversal valve (2) can connect with first pump (4),
The first outlet of first reversal valve (2) is used to connect the steering of vehicle, the second outlet of first reversal valve (2)
Connected with the pressure-control valve (15), second reversal valve (9) is with import, first outlet and second outlet, described
The import of two reversal valves (9) can be connected with second pump (5), and the first outlet of second reversal valve (9) is used to connect
The steering of vehicle, the second outlet of second reversal valve (9) is used to connect fluid tank (7),
The steering control valve (30) with first state and the second state,
In the first state, the import of first reversal valve (2) is turned on the first outlet of first reversal valve (2),
The import of second reversal valve (9) is turned on the second reversal valve (9) first outlet, so that the first pump (4) and described
Two pumps (5) provide hydraulic fluid to the steering；
In second state, the import of first reversal valve (2) goes out with the first reversal valve (2) first outlet and second
Mouth is both turned on, so that the pressure-control valve (15) controls the first outlet of first reversal valve (2) to the steering
The pressure of the hydraulic fluid of output.
2. automobile hydraulic system according to claim 1, it is characterised in that the pressure-control valve (15) is including back pressure
Valve.
3. automobile hydraulic system according to claim 1, it is characterised in that first reversal valve (2) also has control
Fluid intake, the control fluid intake is used to introduce the hydraulic fluid of the first pump (4) output, with the hydraulic fluid
Pressure the import of first reversal valve (2) and the first reversal valve (2) first outlet and the are caused when being higher than predetermined value
Two outlets are both turned on.
4. automobile hydraulic system according to claim 3, it is characterised in that first reversal valve (2) includes the first ratio
Example reversal valve, first reversal valve (2) includes the first valve element (26), and first valve element (26) is changed with only making described first
The first position turned on import to the first outlet of valve (2) and the first outlet and second for making first reversal valve (2) go out
Mouth with import turn on the second place, first valve element (26) at the first position, first reversal valve (2)
Pressure of the pressure of first outlet output hydraulic pressure fluid less than the hydraulic fluid that the first reversal valve (2) import is introduced.
5. automobile hydraulic system according to claim 4, it is characterised in that
First reversal valve (2) also includes the first chamber of the first end for being arranged on the first valve element (26) and is arranged on described the
The inlet communication of the second chamber at the second end of one valve element (26), the first chamber and the first reversal valve (2), to introduce institute
State the hydraulic fluid that the first valve element (26) is pushed to the first position, the second chamber and first reversal valve (2)
First outlet is connected, to introduce the hydraulic fluid that first valve element (26) is pushed to the second place.
6. automobile hydraulic system according to claim 5, it is characterised in that second reversal valve (2) also includes first
Elastomeric element (27), first elastomeric element (27) is arranged in the second chamber.
7. automobile hydraulic system according to claim 1, it is characterised in that second reversal valve (9) also includes control
Fluid intake, the control fluid intake is used to introduce the hydraulic fluid of the first pump (4) output, with the hydraulic fluid
Pressure cause that the import of second reversal valve (2) is turned on first outlet when being less than predetermined value.
8. automobile hydraulic system according to claim 7, it is characterised in that second reversal valve (9) includes the second valve
Core (29), be arranged on second valve element (29) first end the 3rd chamber and be arranged on the second of second valve element (29)
4th chamber at end, second valve element (29) is with turn on the import of the second reversal valve (9) and first outlet first
Put and make the second place of import and second outlet conducting, the first outlet of the 3rd chamber and first reversal valve (2)
Conducting, to introduce the hydraulic fluid that second valve element (29) is pushed to its second place, the 4th chamber and described the
The import conducting of two reversal valves (2), to introduce second valve element (29) is pushed to the first position of second valve element
Hydraulic fluid.
9. automobile hydraulic system according to claim 8, it is characterised in that second reversal valve (9) also includes second
Elastomeric element (210), second elastomeric element (210) is arranged in the 3rd chamber.
10. automobile hydraulic system according to claim 1, it is characterised in that second reversal valve (9) includes the second ratio
Example reversal valve.
11. a kind of engineering trucks, it is characterised in that including the automobile hydraulic system described in claim 1 to 10.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710029806.7A CN106762928B (en) | 2017-01-17 | 2017-01-17 | Automobile hydraulic system and engineering truck with it |
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| CN201710029806.7A CN106762928B (en) | 2017-01-17 | 2017-01-17 | Automobile hydraulic system and engineering truck with it |
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| CN106762928B CN106762928B (en) | 2018-10-16 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111794958A (en) * | 2020-07-16 | 2020-10-20 | 潍柴动力股份有限公司 | Hydraulic pump and vehicle with same |
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| WO2014097423A1 (en) * | 2012-12-19 | 2014-06-26 | 株式会社 島津製作所 | Hydraulic circuit and cargo-handling vehicle |
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| CN102229328A (en) * | 2011-05-05 | 2011-11-02 | 四川大学 | Vehicle mechanical energy-saving hydraulic system with multi-pump confluence |
| CN102434502A (en) * | 2011-12-23 | 2012-05-02 | 四川大学 | Frequency-conversion pump controlled steering hydraulic system for loader |
| CN103085865A (en) * | 2012-11-30 | 2013-05-08 | 广西柳工机械股份有限公司 | Load sensitive turning hydraulic system of loading machine |
| CN103016457A (en) * | 2012-12-05 | 2013-04-03 | 中联重科股份有限公司 | Hydraulic pump control system, vehicle and steering hydraulic system of vehicle |
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| CN106762928B (en) | 2018-10-16 |
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Effective date of registration: 20220729 Address after: 221004 26 Tuo Lan Shan Road, Xuzhou economic and Technological Development Zone, Jiangsu Patentee after: JIANGSU XUGONG ENGINEERING MACHINERY RESEARCH INSTITUTE Co.,Ltd. Address before: 221004 Industrial Zone, Xuzhou Economic Development Zone, Jiangsu, China Patentee before: XCMG CONSTRUCTION MACHINERY Co.,Ltd. |