CN201280153Y - Vehicle hydraulic system with pressure release valve - Google Patents
Vehicle hydraulic system with pressure release valve Download PDFInfo
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- CN201280153Y CN201280153Y CNU2008201163557U CN200820116355U CN201280153Y CN 201280153 Y CN201280153 Y CN 201280153Y CN U2008201163557 U CNU2008201163557 U CN U2008201163557U CN 200820116355 U CN200820116355 U CN 200820116355U CN 201280153 Y CN201280153 Y CN 201280153Y
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Abstract
The utility model relates to a vehicle hydraulic system with a pressure relief valve. The vehicle hydraulic system comprises a hydraulic pump, an optional diverter valve, a first hydraulic load, a pressure relief valve, and a second hydraulic load serially connected with the main fluid channel. When the pressure of the hydraulic fluid in the main fluid channel between the hydraulic pump and the first hydraulic load rises to a first threshold, the diverter valve, if present, is enabled to divert the hydraulic fluid pumped by the hydraulic pump to a first fluid flow communicated with the main fluid channel of the first hydraulic load and a second fluid flow communicated with the main fluid channel between the first load and the pressure relief valve; the pressure relief valve can limit the highest pressure of the hydraulic fluid discharged from the pressure relief valve to a second threshold smaller than the first threshold; and the first hydraulic load and the second hydraulic load can be a hydraulic brake boosting device and a hydraulic steering gear device.
Description
The cross reference of related application
The application advocates the preceence that the U.S. Provisional Application of application on September 20th, 2006 number is 60/846004, name is called the application of the automobile hydraulic system with reducing valve according to united states patent law 35U.S.C.119 (e), and the disclosed content of this application is herein in conjunction with as a reference.
Technical field
The utility model relates to a kind of automobile hydraulic system, particularly has the hydraulic efficiency pressure system of hydraulic fluid pump and at least one hydraulic efficiency gear.
Background technology
Many trucies with hydraulic brake system, the truck of particularly large-scale petrol power and diesel comprises the hydraulic braking ancillary system, rather than is included in normally used vacuum brake ancillary system in the Passenger motor vehicle.Use the vacuum brake ancillary system to have a lot of problems in the vehicle that uses TC engine, such vehicle uses the hydraulic braking ancillary system usually.In addition, has the demand of secondary market, such as not having brake auxiliary device or using the vacuum brake ancillary system automobile of some problems to occur for the hydraulic braking ancillary system of vehicle.Such hydraulic braking ancillary system is well-known and sells at commercial field.
Typically, these hydraulic braking ancillary systems are connected in series between steering gear and Hydraulic Pump, use the fluid generation of pump to offer the auxiliary needed pressure of braking.The fluid that pump comes is limited in the less narrow scope of flow velocity usually, can not change the variation of satisfying vehicle working condition wittingly.Because series connected setting, the joint of the application of braking and hydraulic braking ancillary system can influence the flow velocity of hydraulic fluid to steering gear, and therefore influence is for the effectively auxiliary amount of steering gear.Especially, when needs apply bigger deceleration loading, can cause the increase for the feedback pressure of pump, the decompression threshold value that exceeds pump (for example, 1500psi).On such level, the part that pump bypass is opened the fluid that will flow out forwards the inlet of pump to, and the pressure that its circulation can be performed until brake auxiliary device is lower than the threshold value of bypass disc.Under the situation of decompression, the flow that fluid reduces is sent to steering gear, and this rotary action that will cause under the situation of extreme decompression operator by vehicle to operate steering wheel rotation can be realized obvious increase.
In order to alleviate such situation to small part, flow divider valve or priority valve can be set in hydraulic efficiency pressure system the part from pump to the steering gear fluid discharged under the condition of starting building than recasting is shifted.The content description that U.S. Patent application No.6814413B2 discloses use such shunting and at this in conjunction with as a reference.When transferring to the steering gear auxiliary device at the fluid that uses diverter that part is discharged from pump under the heavier damped condition and having clear superiority; use such diverter also to need the steering gear device to have reducing valve usually, at least with the pressure relief value sizableness of brake auxiliary device.
Usually, some are compared with the needed brake auxiliary device of same vehicle for the enough steering gear auxiliary devices of special car and have lower pressure relief value.Therefore, the steering gear auxiliary device has at least the needs with the pressure relief value of the identical size of pressure relief value of brake auxiliary device, can directly influence the selection of steering gear auxiliary device and cause selecting more expensive steering gear auxiliary device usually.
The utility model content
The utility model provides a kind of hydraulic braking and steering assist system, and this system has guide valve and the reducing valve that allows the steering gear device and have lower pressure relief value with respect to the brake auxiliary device of the setting of connect with brake auxiliary device.
The utility model comprises, wherein also has other form, automobile hydraulic system, this system comprises according to series connected and be arranged on along the hydraulic circuit of main fluid passage according to consecutive order, this loop comprises Hydraulic Pump, first hydraulic load, reducing valve and second hydraulic load, and wherein the hydraulic fluid pressure of the main fluid passage between the Hydraulic Pump and first hydraulic load can rise to first threshold value.To second threshold value, wherein first threshold value is higher than second threshold value from the top pressure of the hydraulic fluid of reducing valve discharging for reducing valve restriction.
Wherein a kind of form of the utility model comprises, automobile hydraulic system, this system comprises that this loop comprises Hydraulic Pump, flow divider valve, first hydraulic load, reducing valve and second hydraulic load according to series connected and be arranged on along the hydraulic circuit of main fluid passage according to consecutive order.Under first operating mode, all pass flow divider valve fully from the Hydraulic Pump fluid discharged and arrive first hydraulic load along the main thoroughfare, pass reducing valve and arrive second hydraulic load and turn back to Hydraulic Pump.When the hydraulic fluid pressure of the main thoroughfare between the Hydraulic Pump and first hydraulic load is thus lifted to first threshold value, the fluid of first fluid stream and second fluid stream is injected in the flow divider valve shunting by Hydraulic Pump, this first fluid stream is got in touch with the main flow channel of the first hydraulic load upstream, a bit getting in touch in the main fluid passage of this second fluid stream and the first hydraulic load downstream and reducing valve upstream.To second threshold value, wherein first threshold value is greater than second threshold value from the maximum pressure of the hydraulic fluid of reducing valve discharging for reducing valve restriction.
In embodiment more of the present utility model, first hydraulic load can adopt the hydraulic braking booster device, and second hydraulic load can adopt the fluid-link steering wheel word, therefore provide having the brake servo unit that series connection is provided with and the automobile hydraulic system of steering gear, wherein steering gear has lower pressure relief value with respect to brake servo unit.
An advantage of the present utility model is, provides that a kind of effectively and the relative simply automobile-used hydraulic efficiency pressure system of hydraulic pressure this system comprises first hydraulic load, and this load has bigger decompression with respect to second hydraulic load that is connected in series with first load.
Other advantage of the present utility model is the combination that allows steering gear auxiliary device and brake auxiliary device, wherein the steering gear auxiliary device has lower hydraulic pressure pressure relief value, therefore and saved cost with respect to automobile hydraulic system with steering gear auxiliary device, this steering gear auxiliary device has than at least with the cooresponding required pressure relief value of the decompression of brake auxiliary device and the value of Yan Gengda.
Description of drawings
Subsequently in conjunction with the accompanying drawings to the description of embodiment of the present utility model, above-mentioned feature of the present utility model and other features will become very clear by reference, and it is easier to understand that utility model itself also will become, wherein:
Accompanying drawing 1 is the scheme drawing according to hydraulic efficiency pressure system of the present utility model.
Accompanying drawing 2 is the priority valve under the normal fluid operating mode or the part sectional view of split channel.
Accompanying drawing 3 is part sectional views of the priority valve shown in the accompanying drawing 2, and wherein priority valve is just by C part water diversion part fluid.
Accompanying drawing 4 is part sectional views of reducing valve under the normal fluid operating mode.
Accompanying drawing 5 is part sectional views of reducing valve under the high pressure operating mode.
Identical Reference numeral is represented identical parts in each view.Though it is the example of Zhan Shiing has shown a kind of embodiment of the present utility model in one way here, that the following content that discloses can not be thought limit or be interpreted as the utility model is restricted to disclosed accurate form.
The specific embodiment
Accompanying drawing 1 shows the hydraulic efficiency pressure system 10 of vehicle 12, is used for service vehicle and turns to and brake.Hydraulic efficiency pressure system comprises Hydraulic Pump 14 and liquid vessel 16.Liquid vessel can be built in the pump 14 as shown in the figure, perhaps arranges away from pump 14.
First and second hydraulic load 22,24 adopt the form of hydraulic efficiency gear or the form of hydraulic pressure branch road.In the embodiment that shows, first load 22 is hydraulic braking ancillary system or booster device, and second load 24 is fluid-link steering gear ancillary system or device.
With reference to accompanying drawing 2 and 3, priority valve 20 comprises the valve body 30 with the valve opening that forms chamber 32,, slidably control valve for fluids parts 34 are mounted in chamber.In valve body 30, have a lot of ports, be identified as A, B, C, D port in the accompanying drawings.Fluid is directed into the valve body 30 by the A port from pump 14, and wherein fluid enters into chamber 32 and derived valve body 30 by one or more outlet port B, C, D according to the operating mode that will describe,
Accompanying drawing 2 has shown at the feedback pressure from brake auxiliary device 22 and has been lower than under the operating mode of predefined threshold value or control presssure the normal running of priority valve 20.All fluids that enter the A port flow through by the main thoroughfare 35 in the hole 32 of diverter 20, and arrive hydraulic braking servo-unit 22 by the B port.Certainly, for the device of all reality, because the tolerance between each parts can produce some inevitable flow losses.
Under the operating mode shown in the accompanying drawing 2, braking auxiliary 22 is under predetermined threshold value or operate under pressure relief value, and fluid can flow freely into the A port and flow out the B port by pipeline 35.As shown in the figure, valve body 30 can be equipped with piecing devices 36, and this device extends into valve opening 32, and the direct UNICOM between trunk line formation and the valve opening 32.Line pressure within the trunk line 35 feeds back to control valve for fluids 34 by P hole cutoff port 38 in decompression or the piecing devices 36 and the communication passage 40 in the valve body 30.This pressure, the bias current control cock parts 34 that apply together with the fluid controlling spring withstand piecing devices 36.In this position, valve member 34 covers C, D port fully to turning to auxiliary 24 and the passage of reservoir 16, and respectively, such fluid neither enters and also do not leave this two passages.Valve member 34 has reservoir pressure UNICOM groove 44, and this groove is arranged at the D port usually, and therefore no matter how the position of valve member 34 all is exposed to reservoir pressure.This reservoir pressure is by the inside UNICOM of opening 46 with valve.Little poppet valve 50 with the fluid under the reservoir pressure of the fluid under the line pressure after the valve member 34 within the valve member 34 separately.
With reference now to accompanying drawing 3,, shown such situation, wherein braking aux. pressure that is formed in the B port by brake auxiliary device 22 and main thoroughfare 35 have surpassed 22 predetermined threshold force value of brake auxiliary device, and this value is preferably selected under the pressure relief value of pump 14.Along with the feedback pressure in the main thoroughfare 35 near predetermined control pressure, to leave the lifting ball 52 of poppet valve 50 with the fluid pressure of control valve for fluids dorsal part conducting, this will cause that hydraulic oil flows out and flows to reservoir 16 by opening the valve member 34 46 and D port after the piston 54 of valve member 34.Because P hole cutoff port 38 is very little, if poppet valve 50 be open and emit hydraulic oil from primary piston 54, communication passage pressure 40 will be lower than the line pressure in the main thoroughfare 35.This difference of pressure will cause that piston 54 overcomes spring 42 and gets back to the position shown in the accompanying drawing 3 from the slip of the position shown in the accompanying drawing 2, therefore, the C port is exposed to the main fluid that is pumped by pump 14 of passing the A port and coming flow.Therefore the fluid that comes from pump 14 that passes the A port will offer B partial sum C port, and clearly, the major part of fluid will flow out and be transferred to steering gear device 24 by hydraulic channel 25 from the C port by brake auxiliary device 22.When the feedback pressure that braking force control system 22 produces was elevated to predetermined control pressure, control valve for fluids 34 therefore operation came self-measuring to pass through the fluid of the surplus oil of C port, and the control presssure of mentioning here preferably is chosen under the decompression pressure of pump 14.
Priority valve with different structure can be applied in the utility model, and such mechanism shifts hydraulic fluid, and the fluid that is transferred is by brake auxiliary device 22 and be sent to and turn to auxiliary device 24.The priority valve that for example has simplified structure has been No.11/901821 by people such as Wong in Application No., " automobile hydraulic system " by name with priority valve and reducing valve, Agt's application case numbering DP-315726's, advocate in the utility patent file of preceence of U. S. application No.60/845911 provisional application of on September 20th, 2006 application, and people such as Wong is No.11/901822 in Application No., " automobile hydraulic system " by name with priority valve, Agt's application case numbering DP-315727's, advocate to be described in the utility patent file of preceence of U. S. application No60/845892 provisional application of on September 20th, 2006 application, these utility patent application all have the identical applying date with the application, therefore, two utility patents and two provisional application are all sold to the application's cessionary, therefore, each in four utility patents and the provisional application is all herein in conjunction with as a reference.
Reducing valve 60 is arranged in hydraulic tubing 25, and this pipeline is sent to steering gear auxiliary device 24 with hydraulic fluid from brake auxiliary device 22 and C port.The guiding valve that graphic reducing valve 60 is pilot operationps also was arranged in the pipeline 25 before steering gear device 24.Valve 60 comprises the valve body 62 of the G (guiding port) that limits valve chamber 62 and port E (ingress port), F (outlet port) and open to chamber interior.Thread plug or parts 78 have hole 80, extend on this Kong Zaiqi length and have set H port (low-pressure port).As shown in Figure 1, converge and enter into valve chamber 62 from the port C of priority valve 20 fluid that comes out and the fluid that from brake auxiliary device 22, flows out by the E port.Fluid flows out through the F port from valve chamber 62.When the fluid pressure of guiding pipeline 58 conducting hydraulic tubings 56 time the G port, the fluid of hydraulic tubing 56 conductings from the F port to steering gear device 24.Hydraulic tubing 82 provides the fluid communication between H port and reservoir 16.
Valve 60 generally includes the double end spool member 64 that is positioned at valve chamber 62.Spool member 64 comprises the first piston head 66 and second piston head 68.The first piston head 66 and second piston head 68 are sealed and matched with the sidewall of valve chamber 62, and valve chamber 62 are divided into middle body 70, leader 72 and low-pressure section 74 hermetically.By when shown in the figure being helical spring bias component 76 joints, first piston head 66 is in the face of the G port at second piston head 68.Thread plug 78 is positioned at the open end of valve chamber 62 and engages with the opposite ends of spring 76.
Under the low pressure situation, as shown in Figure 4, first piston head 66 stops a part or the part of F port also not to stop.Under this low pressure situation, the fluid that enters by the E port enters into the middle body 70 of valve chamber 62, bar 67 round the spool member 64 that connects the first piston head 66 and second piston head 68 flows, and causes having only when flowing through valve 60 minimum pressure to reduce by F is partly mobile.When with the pipeline 56 of the inlet conducting that turns to auxiliary device 24 in pressure when increasing with respect to the fluid pressure in the low-pressure section 74, because load is placed on the device 24 or because other, the increase of this pressure is partly conducted to the G as first piston head 66 by pipeline 58.Fluid pressure in the leader 72 of valve chamber 62 with spool member 64 under spring 76 and low pressure fluid or spring members 74 is that apply and the opposite sense upper offset of the bias force that the pressure of reservoir 16 size is approximate.Along with the increase of the pressure in guide member 72, spool member 64 is as shown in Figure 5 to stopper 78 biasings.Along with spool member 64 is slided to stopper 78, first piston head 66 is further blocked the E part, therefore limit fluid is by valve 60, and caused sharply reducing of fluid pressure by valve 60, and is used for limiting the maximum pressure to the hydraulic tubing 56 that turns to auxiliary device 24 feed streams.As mentioned above, therefore valve 60 limits the pressure that flows through fluid therebetween and sets the maximum pressure that passes through the fluid of F port outflow from valve 60.Therefore, valve 60 can be selected, and the fluid maximum pressure in the hydraulic tubing 56 is less than the permission maximum pressure of the hydraulic fluid that enters into brake auxiliary device 22 like this.Thus, hydraulic efficiency pressure system 10 can be used the steering gear device 24 with pressure limit value littler than the force value of brake auxiliary device 22.
As top disclosed content was illustrated, hydraulic circuit 10 comprised, series connection be provided with consecutive order, Hydraulic Pump 14, flow divider valve 20, brake booster device 22, reducing valve 60, steering gear device 24 and reservoir 16.When like that the part of fluid being shunted with bypass brake servo unit 22 by the C port that diverter 20 does not take place when brake servo unit 22 produces higher relatively feedback pressure, will be from most fluids that pump 14 discharges along the main fluid channel flow, this passage extends from the outlet of pump 14, through discharge conduit 18, through valve 20 from the A port to the B port, to brake servo unit 22, E port to valve 60, by valve from the E port to the F port, arrive steering gear 24 by pipeline 56, arrive reservoir 16, then arrive the inlet of pump 14, circulating in pump 14 is repeated.As mentioned above, when the boost in pressure of brake servo unit 22 upstreams time first threshold value, flow divider valve 20 shunting fluid, a part by with the main fluid passage of brake servo unit 22 upstreams in the conducting of B port, another part of fluid be delivered to by the C port in the main fluid passage of brake servo unit 22 downstreams and valve 60 upstreams a bit.
Should be noted in the discussion above that the reducing valve shown in accompanying drawing 4,5 is an adjustable valve, comprise stopper 78 with the screw thread that connects valve 60 and circuit 82 upper-parts.The characteristic threads of stopper 78 allows the outside adjustment of valve 60 and the situation that valve 60 further limits the F ports.The rotation of stopper 78 causes the longitudinal travel of stopper 78 and axially relocating of spring 42, so regulating spring 42 is applied to the bias force on the spool member 64, therefore regulates the fluid maximum pressure value that discharges from valve 60.Can in the utility model, be used in combination non-adjusting reducing valve and the various reducing valve that can replace.
Though come as a reference the utility model is illustrated, can also combine with other hydraulic efficiency gear and system in conjunction with having the two hydraulic efficiency pressure system of axial gears auxiliary device and brake auxiliary device.For example, the independent hydraulic fluid pump of known employing comes to provide power to second fluid motor that turns to the auxiliary device HM Hydraulic Motor and have a radiator cooling fan.U.S. Patent No. 5802848 for example, discloses and has brake auxiliary device and be equipped with the system of radiator cooling fan that the fluid motor of power is provided by independent hydraulic pressure, at this in conjunction with as a reference.In alternative embodiment of the present utility model, being provided with of priority valve disclosed herein and reducing valve can be used for independent hydraulic fluid pump easy to use provides power to the fluid motor that turns to auxiliary device and radiator cooling fan.
Further, being provided with of the priority valve of native system and reducing valve (for example can be used for control and two hydraulic efficiency gear, BAS (Brake Assist System), steering assist system, radiator fan or other hydraulic efficiency gear with fluid motor) or two fluid streams that hydraulic circuit is relevant, the wherein setting of priority valve and reducing valve and two related hydraulic efficiency gear or loop, the part of a large complicated hydraulic circuit of formation.
In an other embodiment, reducing valve can be used to not have the relief circuit of priority valve to limit the fluid pressure that offers steering gear auxiliary device or other hydraulic efficiency gear.For example, reducing valve can be used for, and has brake auxiliary device and turns to the equipment gear device still not have the whole hydraulic efficiency gear of priority valve, makes to use to have the auxiliary device that turns to that has low decompression with respect to brake auxiliary device.Perhaps, reducing valve can be used for the steering gear auxiliary device as described herein in traditional hydraulic circuit, and this steering gear auxiliary device does not comprise that any other hydraulic efficiency gear is limited to the pressure of the hydraulic fluid of steering gear auxiliary device inlet.
, the utility model illustrates that the utility model can further change not breaking away from the scope of disclosure though having concrete example here.Therefore the application can comprise modification, use or the application of any use general principles of the present utility model.
Claims (15)
1, automobile hydraulic system comprises:
Hydraulic circuit, this loop comprise, along the main fluid passage according to series connected and be provided with according to consecutive order, Hydraulic Pump, first hydraulic load, reducing valve and second hydraulic load,
It is characterized in that the hydraulic fluid pressure of the main fluid passage between the Hydraulic Pump and first hydraulic load can rise to first threshold value,
To second threshold value, wherein said first threshold value is higher than described second threshold value to the restriction of wherein said reducing valve from the top pressure of the hydraulic fluid of reducing valve discharging.
2, automobile hydraulic system as claimed in claim 1 is characterized in that, described first hydraulic load is that hydraulic braking booster device and described second hydraulic load are the fluid-link steering wheel words.
3, automobile hydraulic system as claimed in claim 2, it is characterized in that, described reducing valve comprises the valve body that defines the valve chamber valve chamber, is slidingly arranged in the spool member in the described valve chamber, this spool member has first valve head and second valve head, described first and second valve heads engage with described valve seal, and described valve chamber are divided into middle body, leader and feedback line part hermetically;
Described valve chamber has that ingress port receives from described main fluid passage and the fluid that comes, has the outlet port, drain into described main fluid passage through the described fluid of this outlet port, have the described main fluid passage fluid communication of guiding port and described reducing valve downstream and described steering gear upstream, have the main fluid passage fluid communication of feedback line port and described steering gear downstream and described Hydraulic Pump upstream;
Described ingress port and outlet port each all respectively with the described middle body fluid communication of described valve chamber, described guiding port and described leader fluid communication, and described feedback line port and described feedback line segment fluid flow UNICOM; And
Wherein with respect to the increase of the fluid pressure of the described leader of described feedback line part, can relatively move described spool member and therefore limit fluid flow through from described reducing valve, and reduce pressure by the hydraulic fluid of described outlet port discharging.
4, automobile hydraulic system as claimed in claim 3 is characterized in that, further comprises helical element and can operate the bias component that engages with described spool member and described helical element; Adjust the operable position of described bias component and therefore adjust described second threshold value with the outside adjustment of described helical element.
5, automobile hydraulic system as claimed in claim 3 is characterized in that, further comprises the hydraulic pressure reservoir, with the position UNICOM of described main fluid passage in the upstream of the downstream of described steering gear and described Hydraulic Pump.
6, automobile hydraulic system as claimed in claim 3 is characterized in that, described Hydraulic Pump is with substantially invariable flow velocity release of hydraulic fluid.
7, automobile hydraulic system as claimed in claim 3 is characterized in that, further comprises the flow divider valve in the described hydraulic circuit of the upstream that is arranged in described Hydraulic Pump downstream and described brake servo unit;
Wherein, under the first operation operating mode, all substantially hydraulic fluids by described Hydraulic Pump discharging pass through described flow divider valve along described main thoroughfare, arrive described brake servo unit, through described reducing valve, arrive described steering gear and turn back to described Hydraulic Pump; And
Wherein, when the hydraulic fluid pressure in the main fluid passage between described Hydraulic Pump and described first hydraulic load was elevated to described first threshold value, the shunting of described flow divider valve is entered into the first fluid stream of the described main fluid passage UNICOM of the described first hydraulic load upstream with second fluid of some UNICOMs of the described main fluid passage of described first hydraulic load downstream and described reducing valve upstream by the hydraulic fluid of described Hydraulic Pump discharging flowed.
8, automobile hydraulic system as claimed in claim 7, it is characterized in that, described Hydraulic Pump is with substantially invariable flow velocity release of hydraulic fluid, described hydraulic circuit further comprises the hydraulic pressure reservoir with the described main fluid passage fluid communication of described steering gear downstream and described Hydraulic Pump upstream, and wherein the hydraulic fluid pipeline with the fluid pressure in the described hydraulic pressure reservoir and described flow divider valve, described brake servo unit, described reducing valve and described steering gear UNICOM.
9, automobile hydraulic system as claimed in claim 8 is characterized in that, further comprises helical element and can operate the bias component that engages with described spool member and described helical element; Adjust by described bias component with the outside adjustment of described helical element and to be applied to bias force on the described spool member, and therefore adjust described second threshold value.
10, automobile hydraulic system comprises:
Hydraulic circuit, this loop comprise, along the main fluid passage according to series connected and Hydraulic Pump, flow divider valve, first hydraulic load, reducing valve and second hydraulic load are set according to consecutive order;
It is characterized in that, under the first operation operating mode, all substantially hydraulic fluids by described Hydraulic Pump discharging pass through described flow divider valve along described main thoroughfare, arrive described first hydraulic load, through described reducing valve, arrive described second hydraulic load and turn back to described Hydraulic Pump; And
Wherein, when the hydraulic fluid pressure in the main fluid passage between described Hydraulic Pump and described first hydraulic load was elevated to described first threshold value, the shunting of described flow divider valve is entered into the first fluid stream of the described main fluid passage UNICOM of the described first hydraulic load upstream with second fluid of some UNICOMs of the described main fluid passage of described first hydraulic load downstream and described reducing valve upstream by the hydraulic fluid of described Hydraulic Pump discharging flowed.
To second threshold value, wherein said first threshold value is higher than described second threshold value to the restriction of wherein said reducing valve from the top pressure of the hydraulic fluid of reducing valve discharging.
11, automobile hydraulic system as claimed in claim 10 is characterized in that, described first hydraulic load is that hydraulic braking booster device and described second hydraulic load are the fluid-link steering wheel words.
12, automobile hydraulic system as claimed in claim 11, it is characterized in that, described reducing valve comprises the valve body that limits valve chamber, is slidingly arranged in the spool member in the described valve chamber, this spool member has first valve head and second valve head, described first and second valve heads engage with described valve seal, and described valve chamber are divided into middle body, leader and feedback line part hermetically;
Described valve chamber has that ingress port receives from described main fluid passage and the fluid that comes, has the outlet port, drain into described main fluid passage through the described fluid of this outlet port, have the described main fluid passage fluid communication of guiding port and described reducing valve downstream and described steering gear upstream, have the main fluid passage fluid communication of feedback line port and described steering gear downstream and described Hydraulic Pump upstream;
Described ingress port and outlet port each all respectively with the described middle body fluid communication of described valve chamber; Described guiding port and described leader fluid communication, and described feedback line port and described feedback line segment fluid flow UNICOM; And
Wherein with respect to the increase of the fluid pressure of the described leader of described feedback line part, can relatively move described spool member and therefore limit fluid flow through from described reducing valve, and reduce pressure by the hydraulic fluid of described outlet port discharging.
13, automobile hydraulic system as claimed in claim 12 is characterized in that, further comprises helical element and can operate the bias component that engages with described spool member and described helical element; Adjust the operable position of described bias component and therefore adjust described second threshold value with the outside adjustment of described helical element.
14, automobile hydraulic system as claimed in claim 12 is characterized in that, further comprises the hydraulic pressure reservoir, with the position UNICOM of described main fluid passage in the upstream of the downstream of described steering gear and described Hydraulic Pump.
15, automobile hydraulic system as claimed in claim 12 is characterized in that, described Hydraulic Pump is with substantially invariable flow velocity release of hydraulic fluid.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US11/901,949 US20080066990A1 (en) | 2006-09-20 | 2007-09-19 | Vehicular hydraulic system with pressure reducing valve |
| US11/901949 | 2007-09-19 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201280153Y true CN201280153Y (en) | 2009-07-29 |
Family
ID=40927037
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008201163557U Expired - Fee Related CN201280153Y (en) | 2007-09-19 | 2008-04-29 | Vehicle hydraulic system with pressure release valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201280153Y (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102229328A (en) * | 2011-05-05 | 2011-11-02 | 四川大学 | Vehicle mechanical energy-saving hydraulic system with multi-pump confluence |
| CN110469647A (en) * | 2019-06-28 | 2019-11-19 | 中冶宝钢技术服务有限公司 | A kind of anti-overspeed hydraulic device for hydrostatic driving vehicle |
| CN111186483A (en) * | 2020-02-28 | 2020-05-22 | 山东交通学院 | Steering hydraulic pump suitable for heavy vehicle emergency working condition |
| CN114352779A (en) * | 2021-12-03 | 2022-04-15 | 西安航空制动科技有限公司 | Fixed value pressure reducing valve for aviation braking system |
-
2008
- 2008-04-29 CN CNU2008201163557U patent/CN201280153Y/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102229328A (en) * | 2011-05-05 | 2011-11-02 | 四川大学 | Vehicle mechanical energy-saving hydraulic system with multi-pump confluence |
| CN102229328B (en) * | 2011-05-05 | 2013-05-08 | 四川大学 | Vehicle mechanical energy-saving hydraulic system with multi-pump confluence |
| CN110469647A (en) * | 2019-06-28 | 2019-11-19 | 中冶宝钢技术服务有限公司 | A kind of anti-overspeed hydraulic device for hydrostatic driving vehicle |
| CN111186483A (en) * | 2020-02-28 | 2020-05-22 | 山东交通学院 | Steering hydraulic pump suitable for heavy vehicle emergency working condition |
| CN114352779A (en) * | 2021-12-03 | 2022-04-15 | 西安航空制动科技有限公司 | Fixed value pressure reducing valve for aviation braking system |
| CN114352779B (en) * | 2021-12-03 | 2023-12-29 | 西安航空制动科技有限公司 | Constant pressure reducing valve for aviation brake system |
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