CN105235665B - A kind of all-hydraulic double loop non-muscular energy braking system - Google Patents
A kind of all-hydraulic double loop non-muscular energy braking system Download PDFInfo
- Publication number
- CN105235665B CN105235665B CN201510700790.9A CN201510700790A CN105235665B CN 105235665 B CN105235665 B CN 105235665B CN 201510700790 A CN201510700790 A CN 201510700790A CN 105235665 B CN105235665 B CN 105235665B
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- brake
- valve
- braking
- hydraulic
- braking system
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/17—Using electrical or electronic regulation means to control braking
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/17—Using electrical or electronic regulation means to control braking
- B60T8/1755—Brake regulation specially adapted to control the stability of the vehicle, e.g. taking into account yaw rate or transverse acceleration in a curve
Abstract
The invention discloses a kind of all-hydraulic double loop non-muscular energy braking system, including hydraulic circuit, brake valve, non-linear load sensing valve and brake assembly, the brake valve passes sequentially through hydraulic circuit and non-linear load sensing valve is connected with brake assembly, and two valve chambers of the non-linear load sensing valve are connect with four brakes in brake assembly in X-type.The present invention is more close relative to traditional pressure distributing valve and ideal brake braking force partition characteristic, ideal brake braking force distribution can preferably be met to require, the brake efficiency of automobile can be significantly improved, and the synchronous braking of front and back wheel may be implemented, improve the utilization rate of the attachment condition on road surface, improve the balance and stability of wheel braking, braking effect is notable, this double-circuit braking system still has the brake force of half in the case of the partial failure of side, disclosure satisfy that the emergency brake requirement of vehicle.
Description
Technical field
The present invention relates to a kind of all-hydraulic double loop non-muscular energy braking system, are suitable for hydraulic vehicle braking field.
Background technology
All-hydraulic double loop non-muscular energy braking system is the braking system more generally used in automobile market now.Braking system
System will not only ensure directional stability when automobile can reach preferable brake efficiency and braking, be most heavy in active safety system
The system wanted also takes on the task of the brake braking force distribution of each axle of automobile, the brake braking force of each axis
It distributes rationally, directional stability when good brake efficiency and preferable braking can be reached.
If a kind of anti-lock braking system of traditional brake system of car (ABS), main includes four kinds, respectively four-way
Road formula, three-way type, two channel-types and a channel-type, wherein four-way ABS are there are four wheel speed sensors, towards four wheels
In the pipeline of brake cylinder, a brake-pressure controller device is respectively set, is independently controlled, constitutes four-way control form.
But if the attachment coefficient of two wheels of vehicle right and left differs larger (such as road surface part ponding or icing), two vehicles when braking
The ground brake force of wheel just differs larger, can influence the brake direction steady of automobile.And triple channel ABS is carried out to two front-wheels
Independent control, two trailing wheels by it is low select principle carry out together control (i.e. two wheels are controlled by a channel, with ensure adhesive force compared with
Small wheel not locking is principle), also referred to as mixing control, the characteristics of this control is that two trailing wheels select principle to be controlled together by low
When processed, it is ensured that the brake force that automobile controls two trailing wheels under various conditions is equal, even if the attachment coefficient phase of both sides wheel
Difference is larger, and the brake force of two wheels is limited to the smaller level of adhesive force.Since two front wheel brake power imbalances are to automobile
Travel direction stability influence is relatively small, it is necessary to be repaiied on resulting influence by the handling maneuver of driver
Just, braking effect is also to be improved.Two channel-types and a channel-type ABS are difficult in directional stability, course changing control and system
Dynamic efficiency various aspects are taken into account, at present using seldom.
In addition braking system for each wheel braking effect mainly rely on load sensing valve, traditional inductive proportional valve and
The pressure partition characteristic of load sensing pressure limiting valve is essentially all straight line or broken line, and this relations of distribution cannot meet ideal brake
The utilization rate of the requirement of braking force distribution characteristic, ground attaching coefficient is low, therefore there is the main problem of brake efficiency difference, prolongs
The braking distance for having grown automobile reduces the safety of driving.
Invention content
The technical problem to be solved by the present invention is to overcome the deficiencies of existing technologies, a kind of all-hydraulic double loop power is provided
Braking system, it can largely improve the utilization rate of the attachment condition on road surface, improve the brake efficiency of automobile, shorten vapour
The distance of the braking of vehicle.
The present invention solves above-mentioned technical problem and adopts the technical scheme that：A kind of all-hydraulic double loop non-muscular energy braking system,
Including hydraulic circuit, brake valve, non-linear load sensing valve and brake assembly, the brake valve passes sequentially through hydraulic circuit and non-thread
Property load sensing valve is connected with brake assembly；The brake assembly includes near front wheel brake, off-front wheel brake, left rear wheel system
Dynamic device and off hind wheel brake, the non-linear load sensing valve include two valve chambers, front end and the near front wheel system of one of valve chamber
Dynamic device is connected, and rear end is connected with off hind wheel brake, and the front end of another valve chamber is connected with off-front wheel brake, rear end and a left side
Rear wheel brake is connected
Further, in order to provide hydraulic energy to hydraulic circuit, the hydraulic circuit includes fluid reservoir, and is connected with fluid reservoir
Hydraulic pump, the hydraulic pump is connected by two independent circuits with the oil inlet of brake valve.
Further, the hydraulic energy savings in order to generate hydraulic pump in hydraulic circuit gets up, to ensure in engine
Or hydraulic pump shuts down, or in the case of the pump oil conduit failure of hydraulic pump, can still provide for complete system several times
It is dynamic, it is provided with accumulator on every independent circuit.
Further, in order to can observe the pressure condition in accumulator immediately and prevent the feelings of insufficient pressure
Condition is additionally provided with pressure gauge and low pressure warning switch on every independent circuit on rear side of accumulator.
Further, in order to which pressure oil remaining in brake valve after braking is flowed back to fluid reservoir, the brake valve returns
Oilhole is connected directly with fluid reservoir.
Further, bent in order to make the braking force distribution curve of the front and back wheel of automobile more be bonded ideal braking force distribution
Line ensures directional stability when braking again while improving brake efficiency to reach, the oil outlet of the brake valve passes through non-
Linear load sensing valve is connected with brake assemblies.
Further, in order to keep the variation of forward and backward oil liquid pressure in valve chamber to stablize relatively, to ensure in the same circuit
Front and back wheel realizes that synchronous braking, the rear end of the valve chamber are provided with pressure relief vent, and the pressure relief vent is connected with fluid reservoir.
Further, in order to front and back brake braking force partition characteristic can be made to change preferably to carry with load change
The adaptability of high threshold, setting thoughts carry lever on the non-linear load sensing valve, and regulation component, the sense load thick stick are provided in valve chamber
Bar is connected with regulation component.
Further, to realize the braking process of brake, the brake valve includes four brake valve monomers, and is arranged and is making
Epicoele, lumen and cavity of resorption inside dynamic valve monomer, the epicoele and lumen are separated by reaction piston, the lumen and cavity of resorption
It is separated by cavity of resorption piston, the epicoele includes epicoele push rod, epicoele piston, variation rigidity balancing spring, institute successively under upper
It states and is provided with lumen push rod in lumen, reaction piston return spring, the lower intracavitary are provided on the outside of the lumen push rod
It is provided with cavity of resorption return spring.
Further, in order to realize the entrance, outflow and oil return of hydraulic oil in brake valve, the side of the brake valve monomer from
It is disposed with oil return hole, oil outlet and fuel feed hole under upper.
After using above-mentioned technical proposal, the present invention has advantageous effect below：The all-hydraulic double loop power of the present invention
Braking system has many advantages, such as that pressure response is fast, brake boost, and using non-linear load sensing valve, oil liquid pressure partition characteristic is in 1/
The non-linear power function relationship of 2 power changes, and is distributed relative to traditional pressure distributing valve and ideal brake braking force
Characteristic is more close, can preferably meet ideal brake braking force distribution and require, can so greatly improve automobile
Brake efficiency.Four brakes of automobile are connected with the state of X-type by non-linear load sensing valve, front and back wheel may be implemented
Synchronous braking, improve the utilization rate of the attachment condition on road surface, improve the balance and stability of wheel braking, braking effect is aobvious
It writes, can still have the brake force of half, Neng Gouman in the case of the partial failure of side by all-hydraulic double-circuit system
The emergency brake requirement of sufficient vehicle, reduces the labor intensity of driver, improves the safety of driving.
Description of the drawings
Fig. 1 is a kind of structural schematic diagram of all-hydraulic double loop non-muscular energy braking system of the present invention；
Fig. 2 is a kind of structure chart in the single circuit of all-hydraulic double loop non-muscular energy braking system of the present invention；
Fig. 3 is a kind of structure chart of the brake valve of all-hydraulic double loop non-muscular energy braking system of the present invention；
Fig. 4 is the A-A sectional views of Fig. 3；
In figure：1. brake valve, 2. non-linear load sensing valves, 3. fluid reservoirs, 4. hydraulic pumps, 5. accumulators, 6. pressure gauges, 7. is low
Pressure alarm switch, 8. off-front wheel brakes, 9. near front wheel brakes, 10. left rear wheel brakes, 11. off hind wheel brakes, 12.
Valve chamber, 13. brake valve monomers, 14. reaction pistons, 15. cavity of resorption pistons, 16. epicoele push rods, 17. epicoele pistons, 18. become rigid
Degree balancing spring, 19. lumen push rods, 20. reaction piston return springs, 21. cavity of resorption return springs, 22. epicoeles, 23. lumens,
24. cavity of resorption, 25. check valves, 26. front-wheel wheel cylinder pressure regulating cavities, 27. trailing wheel wheel cylinder pressure regulating cavities, 28. throttle valves, 29. senses carry lever,
30. automobile chassis, 31. front wheel brake wheel cylinders, 32. rear wheel brake wheel cylinders, D. oil return holes, C. oil outlets, B.
Fuel feed hole, H. pressure relief vents.
Specific implementation mode
In order that the present invention can be more clearly and readily understood, right below according to specific embodiment and in conjunction with attached drawing
The present invention is described in further detail.
As shown in Figs 1-4, a kind of all-hydraulic double loop non-muscular energy braking system, including it is hydraulic circuit, brake valve 1, non-linear
Load sensing valve 2 and brake assembly, the brake valve 1 pass sequentially through hydraulic circuit and non-linear load sensing valve 2 and brake assembly phase
Even；The brake assembly includes near front wheel brake 8, off-front wheel brake 9, left rear wheel brake 10 and off hind wheel brake
11, the non-linear load sensing valve 2 includes two valve chambers 12, and the front end of one of valve chamber 12 is connected near front wheel brake 8, after
End is connected with off hind wheel brake 11, and the front end of another valve chamber 12 is connected with off-front wheel brake 9, rear end and left rear wheel system
Dynamic device 10 is connected
In order to provide hydraulic energy to hydraulic circuit, the hydraulic circuit includes fluid reservoir 3, and the liquid being connected with fluid reservoir 3
Press pump 4, the hydraulic pump 4 are connected by two independent circuits with the oil inlet of brake valve 1.
In order to the hydraulic energy savings for generating hydraulic pump in hydraulic circuit 4, to ensure in engine or liquid
Press pump 4 shuts down, or in the case of the pump oil conduit failure of hydraulic pump 4, can still provide for complete braking several times, often
It is provided with accumulator 5 on independent circuit described in item.
In order to observe the pressure condition in accumulator 5 immediately and the case where prevent insufficient pressure, every
The rear side of accumulator 5 is additionally provided with pressure gauge 6 and low pressure warning switch 7 on the independent circuit.
In order to which pressure oil remaining in brake valve 1 after braking is flowed back to fluid reservoir 3, the oil return hole D of the brake valve 1
It is connected directly with fluid reservoir 3.
In order to make the braking force distribution curve of the front and back wheel of automobile more be bonded ideal braking force distribution curve, to reach
Ensure that directional stability when braking, the oil outlet of the brake valve 1 pass through non-thread sexy load while improving brake efficiency again
Valve 2 is connected with brake assemblies.
In order to keep the variation of forward and backward oil liquid pressure in valve chamber to stablize relatively, to ensure the front and back wheel in the same circuit
Realize synchronous braking, the rear end of the valve chamber 12 is provided with pressure relief vent H, and the pressure relief vent H is connected with fluid reservoir 3.
In order to which front and back brake braking force partition characteristic can be made to change preferably to improve valve with load change
Adaptability, setting thoughts carry lever 29 on the non-linear load sensing valve 2, and regulation component, the sense load thick stick are provided in valve chamber 12
Bar 29 is connected with regulation component.
To realize the braking process of brake, the brake valve 1 includes four brake valve monomers 13, and is arranged in brake valve
Epicoele 22, lumen 23 inside monomer 13 and cavity of resorption 24, the epicoele 22 and lumen 23 are separated by reaction piston 14, described
Lumen 23 and cavity of resorption 24 are separated by cavity of resorption piston 15, and the epicoele 22 includes that epicoele push rod 16, epicoele are lived successively under upper
17, variation rigidity balancing spring 18 is filled in, is provided with lumen push rod 19 in the lumen 23, the outside of the lumen push rod 19 is provided with
Reaction piston return spring 20 is provided with cavity of resorption return spring 21 in the cavity of resorption 24.
In order to realize the entrance, outflow and oil return of hydraulic oil in brake valve 1, the side of the brake valve monomer 13 from it is upper it
Under be disposed with oil return hole D, oil outlet C and fuel feed hole B.
Embodiment one：
All-hydraulic double-circuit braking system as shown in Figure 1, wherein the brake fluid from fluid reservoir 2 adds by hydraulic pump 4
Flow into accumulator 5 and store after pressure, when brake signal is passed to brake valve 1 by driver's brake pedal, make its into
Oilhole is connected with oil outlet, since four brakes 8,9,10,11 of automobile are connected to the fuel-displaced of non-linear load sensing valve 2 in X-type
On mouth, the high pressure oil from hydraulic pump 4 or accumulator 5 separately flows into each after the pressure distribution of non-linear load sensing valve 2
The wheel cylinder of a wheel drag, to generate braking to wheel.It is residual in brake piping after driver loosens brake pedal
Remaining pressure oil flows back to fluid reservoir 3 by the oil return hole of brake valve 1.It is provided with accumulator 5, hydraulic energy can be put aside, to ensure
It shuts down in engine or hydraulic pump 4, or in the case of pump oil conduit failure, can still provide for braking completely several times.
When hydraulic pump 4 or oil feeding line damage, repeatedly energy storage pressure is too low after braking, and low pressure warning switch 7 connects at this time
Lead to and prompts driver's energy storage pressure insufficient.
Embodiment two：
As shown in Fig. 2, for the structure in single circuit and brake valve in all-hydraulic double-circuit braking system, 4 He of hydraulic pump
Accumulator 5 is communicated by check valve 25 and pipeline with the fuel feed hole of brake valve 1, and 1 oil outlet of brake valve is carried with non-thread sexuality respectively
The front and rear wheel wheel cylinder pressure regulating cavity 26,27 of valve 2 communicates, and the oil return hole of brake valve 1 is communicated with low pressure line.Non-linear load sensing valve 2
Trailing wheel wheel cylinder pressure regulating cavity 27 on pressure relief vent H, it is communicated by a throttle valve 28 with low pressure line.Sense carries lever 29 and passes through
The relative displacement variable signal for receiving automobile chassis 30 and non-linear load sensing valve 2 perceives the load change of automobile indirectly.It drives
When member does not have brake pedal, 1 state of brake valve is as shown in Fig. 2, cavity of resorption piston 15 closes under the action of cavity of resorption return spring 21
The fuel feed hole B of brake valve 1 is closed, therefore the pressure oil from hydraulic pump 4 and accumulator 5 cannot be introduced into braking valve chamber.Brake valve 1
Oil outlet C is communicated with oil return hole D respectively, i.e., the wheel cylinder 31,32 of forward and backward brake is communicated with low pressure oil way, therefore is braked
Relative pressure in wheel cylinder 31,32 is zero, and brake does not generate brake force at this time.
17 1 active forces of epicoele piston are given when driver's brake pedal, and by pedal gear and epicoele push rod 16
Fp', reaction piston 14 and lumen push rod 19 are then transmitted to by variation rigidity balancing spring 18.At the same time, reaction
Piston 14 closes back the oil return hole D of brake valve 1, and lumen push rod 19 pushes cavity of resorption piston 15, opens the oil inlet of respective brake valve 1
Hole B.At this time fuel feed hole B with oil outlet C communicate, high pressure oil is flowed into non-linear load sensing valve 2 from hydraulic pump 4 or accumulator 5
Front and rear wheel wheel cylinder pressure regulating cavity 26,27 is finally flowed into the wheel cylinder 31,32 of forward and backward brake and is carried out to forward and backward wheel
Braking.With the raising for going out oil pressure, reaction piston 14 constantly gos up (variation rigidity balancing spring 18 is further compressed), most
After reach equilbrium position, fuel-displaced pressure level-off.Due to the variation rigidity characteristic of variation rigidity balancing spring 18, goes out oil pressure and step on
Plate power and pedal travel at non-linear increasing function relationship.
Compared with prior art, the all-hydraulic double loop non-muscular energy braking system of the present invention has that pressure response is fast, brake boost
The advantages that, using non-linear load sensing valve, oil liquid pressure partition characteristic changes in the non-linear power function relationship of 1/2 power,
It is more close relative to traditional pressure distributing valve and ideal brake braking force partition characteristic, can preferably it meet ideal
Brake braking force distribution requires, and can so greatly improve the brake efficiency of automobile.By non-linear load sensing valve by vapour
Four brakes of vehicle are connected with the state of X-type, and the synchronous braking of front and back wheel may be implemented, improve the attachment condition on road surface
Utilization rate improves the balance and stability of wheel braking, and braking effect is notable, can be one by all-hydraulic double-circuit system
Side loop still has the brake force of half in the case of failing, disclosure satisfy that the emergency brake requirement of vehicle, reduce driver
Labor intensity, improve the safety of driving.
Particular embodiments described above, pair present invention solves the technical problem that, technical solution and advantageous effect carry out
It is further described, it should be understood that the above is only a specific embodiment of the present invention, is not limited to this
Invention, all within the spirits and principles of the present invention, any modification, equivalent substitution, improvement and etc. done should be included in this hair
Within bright protection domain.
Claims (5)
1. a kind of all-hydraulic double loop non-muscular energy braking system, it is characterised in that：Including hydraulic circuit, brake valve (1), non-thread sexuality
Valve (2) and brake assembly are carried, the brake valve (1) passes sequentially through hydraulic circuit and non-linear load sensing valve (2) and brake group
Part is connected；
The brake assembly include near front wheel brake (8), off-front wheel brake (9), left rear wheel brake (10) and it is right after
Take turns brake (11), the non-linear load sensing valve (2) include two valve chambers (12), the front end of one of valve chamber (12) with it is left front
It takes turns brake (8) to be connected, rear end is connected with off hind wheel brake (11), front end and the off-front wheel of another valve chamber (12) are braked
Device (9) is connected, and rear end is connected with left rear wheel brake (10)；The hydraulic circuit includes fluid reservoir (3), and with fluid reservoir (3)
Connected hydraulic pump (4), the hydraulic pump (4) are connected by two independent circuits with the oil inlet of brake valve (1)；Described in every
It is disposed with accumulator (5) on independent circuit；On every independent circuit pressure is additionally provided on rear side of accumulator (5)
Table (6) and low pressure warning switch (7)；The oil return hole of the brake valve (1) is connected directly with fluid reservoir (3)；The brake valve (1)
Oil outlet (C) be connected with brake assemblies by non-linear load sensing valve (2).
2. a kind of all-hydraulic double loop non-muscular energy braking system according to claim 1, it is characterised in that：Each valve chamber (12)
Rear end be provided with pressure relief vent (H), the pressure relief vent (H) is connected with fluid reservoir (3).
3. a kind of all-hydraulic double loop non-muscular energy braking system according to claim 2, it is characterised in that：The non-thread sexuality
It carries setting thoughts on valve (2) and carries lever (29), regulation component is provided in valve chamber (12), the sense carries lever (29) and pressure regulation group
Part is connected.
4. a kind of all-hydraulic double loop non-muscular energy braking system according to claim 3, it is characterised in that：The brake valve
(1) include four brake valve monomers (13), and epicoele (22), lumen (23) and the cavity of resorption that setting is internal in brake valve monomer (13)
(24), the epicoele (22) and lumen (23) are separated by reaction piston (14), and the lumen (23) and cavity of resorption (24) pass through
Cavity of resorption piston (15) separates, and the epicoele (22) includes epicoele push rod (16), epicoele piston (17), variation rigidity successively under upper
Balancing spring (18), the lumen (23) is interior to be provided with lumen push rod (19), is provided on the outside of the lumen push rod (19) anti-
Piston return spring (20) is acted on, cavity of resorption return spring (21) is provided in the cavity of resorption (C).
5. a kind of brake valve suitable for the all-hydraulic double loop non-muscular energy braking system described in claim 4, it is characterised in that：Often
The side of a brake valve monomer (13) is disposed with oil return hole (D), oil outlet (C) and fuel feed hole (B) under upper, described time
Oilhole (D) is connected with fluid reservoir, and the oil outlet (C) is connected with the fuel feed hole (B) of non-linear load sensing valve (2), the fuel feed hole
(B) it is connected with accumulator (5).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510700790.9A CN105235665B (en) | 2015-10-26 | 2015-10-26 | A kind of all-hydraulic double loop non-muscular energy braking system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510700790.9A CN105235665B (en) | 2015-10-26 | 2015-10-26 | A kind of all-hydraulic double loop non-muscular energy braking system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105235665A CN105235665A (en) | 2016-01-13 |
| CN105235665B true CN105235665B (en) | 2018-10-26 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510700790.9A Active CN105235665B (en) | 2015-10-26 | 2015-10-26 | A kind of all-hydraulic double loop non-muscular energy braking system |
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| CN (1) | CN105235665B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108891395B (en) * | 2018-09-07 | 2023-07-07 | 杭叉集团股份有限公司 | Vehicle and front and rear wheel braking force distribution system thereof |
| CN112026731B (en) * | 2020-08-12 | 2023-09-29 | 安徽江淮重型工程机械有限公司 | Full-vehicle braking system of electric tractor |
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|---|---|---|---|---|
| JPS5568449A (en) * | 1978-11-14 | 1980-05-23 | Mitsuwa Seiki Co Ltd | Load sensing type brake pressure distributing controller |
| CN1316358A (en) * | 2000-04-04 | 2001-10-10 | 黄晓然 | Emergency brake of car |
| CN201099233Y (en) * | 2007-11-12 | 2008-08-13 | 万安集团诸暨汽车零部件有限公司 | Double folding point load-sensing proportion valve |
| CN201099240Y (en) * | 2007-11-01 | 2008-08-13 | 万安集团诸暨汽车零部件有限公司 | Double chamber load-sensing proportion valve |
| CN201143928Y (en) * | 2008-01-17 | 2008-11-05 | 安徽江淮汽车股份有限公司 | Light cargo vehicle brake fluid system with load proportional valve |
| CN203198953U (en) * | 2013-05-09 | 2013-09-18 | 天津市强龙汽车部件有限公司 | Load-sensing proportioning valve |
-
2015
- 2015-10-26 CN CN201510700790.9A patent/CN105235665B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5568449A (en) * | 1978-11-14 | 1980-05-23 | Mitsuwa Seiki Co Ltd | Load sensing type brake pressure distributing controller |
| CN1316358A (en) * | 2000-04-04 | 2001-10-10 | 黄晓然 | Emergency brake of car |
| CN201099240Y (en) * | 2007-11-01 | 2008-08-13 | 万安集团诸暨汽车零部件有限公司 | Double chamber load-sensing proportion valve |
| CN201099233Y (en) * | 2007-11-12 | 2008-08-13 | 万安集团诸暨汽车零部件有限公司 | Double folding point load-sensing proportion valve |
| CN201143928Y (en) * | 2008-01-17 | 2008-11-05 | 安徽江淮汽车股份有限公司 | Light cargo vehicle brake fluid system with load proportional valve |
| CN203198953U (en) * | 2013-05-09 | 2013-09-18 | 天津市强龙汽车部件有限公司 | Load-sensing proportioning valve |
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| CN105235665A (en) | 2016-01-13 |
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