CN201231748Y - Vehicle hydraulic system with priority valve - Google Patents
Vehicle hydraulic system with priority valve Download PDFInfo
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- CN201231748Y CN201231748Y CNU2008200094992U CN200820009499U CN201231748Y CN 201231748 Y CN201231748 Y CN 201231748Y CN U2008200094992 U CNU2008200094992 U CN U2008200094992U CN 200820009499 U CN200820009499 U CN 200820009499U CN 201231748 Y CN201231748 Y CN 201231748Y
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Abstract
The utility model relates to a vehicle hydraulic system provided with a pressure sequence valve and provides a vehicle hydraulic system provided with a pump connected in series, a first hydraulic application device and a second hydraulic application device. A valve is arranged to enable the fluid to flow to the first hydraulic application device through an inlet port, a main flow channel and an outlet port of the valve. The valve comprises a valve body and a valve component which slides axially in a slender valve cavity so that the main flow channel is separated from a low-pressure space. The valve also comprises a low-pressure port and a bypass port. The bypass port is sealed not to be communicated with the valve cavity fluid in a first position; meanwhile, when the valve component is pressed by threshold bias pressure which exceeds the increased fluid pressure in the main flow channel to a second position, the bypass port is communicated with the fluid in the main flow channel. The fluid drained from the bypass port is turned around from the first application device to the second application device.
Description
The cross reference of related application
The utility model require under 35U.S.C119 (e) in application on September 20th, 2006, the U.S. Provisional Patent Application sequence is NO.60/84529's and be entitled as the preceence of the application of " automobile hydraulic system with priority valve ", this content is hereby expressly incorporated by reference.
Technical field
The utility model relates to automobile hydraulic system, relates more specifically to have the hydraulic efficiency pressure system of hydraulic fluid pump and at least two hydraulic efficiency gear or sub-loop.
Background technology
Many trucies with hydraulic brake system, particularly bigger petrol power and diesel truck comprise the hydraulic braking force aid system, rather than the vacuum servo system that has in passenger vehicle usually.Using vacuum boosting braking system in having the vehicle of TC engine may be that this vehicle of problematic while also will often use the hydraulic braking force aid system.In addition, have the requirement vehicle, as high-speed car, the automotive parts market of hydraulic braking force aid system, this vehicle may not have brake booster or use the vacuum servo system to encounter difficulties for this vehicle in addition.This hydraulic booster system is well-known and sell in market.
Typically, the flow that these hydraulic braking auxiliary systems make self-pumping simultaneously that is connected in series between steering gear and Hydraulic Pump provides essential brake boost to produce the pressure that needs.Usually come the flow of self-pumping to be limited at a narrow flow rates and do not change the vehicle operation state that changes to satisfy with the interior while wittingly.Because series connected arrangement, the combination of the application of braking and hydraulic braking force aid system can influence hydraulic fluid to the flowing of steering gear, thereby influences the power-assisted size possible to steering gear.Especially, when executing extra heavy brake load, it causes the increase to the back pressure of pump, and the threshold value hold-off pressure that this back pressure may surpass pump (for example, 1500psi).Surpass this level, the pump bypassing valve is opened the ingress port of getting back to pump with a part that turns to outflow, this place's circulation continue up to from the pressure decay of brake booster below bypass threshold.In the process of these release position, the flow of the minimizing of fluid is transported to steering gear, and this can be caused the increase of monitoring of steering-effecting so that rotate wheel flutter under extreme release position by the operator of vehicle.
In order to relax this state at least in part, can in hydraulic efficiency pressure system, place a flow diverters or priority valve so that will redirect to steering gear under the moving state of recasting from the part of pump fluid discharged flow.The use that US Patent NO.6814413 B2 has introduced this flow flow divider valve comprises this content by reference at this simultaneously.Though disclosed flow diverters is an actv. in US Patent NO.6814413 B2, but they are more complicated on making, therefore, relatively more expensive, just wish for this have in the two the hydraulic efficiency pressure system of brake booster that series connection arranges and power steering device use the valve arrangement of simplifying.
The utility model content
The utility model provides the priority valve with simplified structure, this valve can use in the hydraulic efficiency pressure system with the first hydraulic applications device that series connection arranges and second hydraulic applications device, simultaneously wherein when first hydraulic applications device generation higher back pressure this priority valve turn to a fluid flow to the second hydraulic applications device.
In its a kind of pattern, the utility model comprises an automobile hydraulic system, and this system has hydraulic circuit, and it comprises that series connection is arranged and the main flow passage series sequence in edge is Hydraulic Pump, the first hydraulic applications device and the second hydraulic applications device.This hydraulic circuit also comprises the valve with valve body and valve member.This valve body limits an elongated valve pocket of determining an axis, and wherein this valve member axially is slidably disposed in the valve pocket between first axial location and second axial location and hermetically this chamber is separated into main flow passage and low-voltage space.This valve body also limits an ingress port that is communicated with main flow channel fluid, the outlet port that is communicated with main flow channel fluid, the low-pressure port that is communicated with the low-voltage space fluid and a bypass ports.This bypass ports is arranged on axial midway location, is arranged on the side of bypass ports with low-pressure port and ingress port and outlet port are arranged on the relative axial side of bypass ports.When valve member is that the sealing bypass ports is not communicated with the valve pocket fluid when being in first axial location, bypass ports is communicated with main flow passage fluid when valve member is in second axial location.This valve member moves axially to second axial location from primary shaft to the position when the fluid pressure in the main flow passage is elevated to threshold values.Elongated valve pocket, ingress port, outlet port, bypass ports and low-pressure port are the special-purpose fluid communication channels that is limited by valve.This valve is operationally to be placed in the hydraulic circuit of the pump downstream and the first hydraulic applications device upstream, and wherein main flow passage extends to ingress port from Hydraulic Pump, and the outlet port of main flow passage of process and valve is to the first hydraulic applications device.Bypass ports is communicated with main flow passage fluid and therefore turns to the part of fluid flow to the second hydraulic applications device during above threshold values when the pressure in the main flow channel at the point of the first hydraulic applications device downstream and the second hydraulic applications device upstream.
In some embodiment of the present utility model, this valve is included in the valve member biasing to the biasing member of first axial location and the screw member that combines with biasing member, thereby outside adjusting thread member is just regulated threshold value, places bypass ports at this threshold value place and is communicated with main flow channel fluid.
Still in another embodiment of the present utility model, the first hydraulic applications device is that the hydraulic braking booster device while second hydraulic applications device is the fluid-link steering driving device.
The utility model has the advantages that it provides priority valve to be used to have pump and two hydraulic applications devices that series connection is arranged, the manufacturing complexity of comparing and having reduced this priority valve with the known pressure sequence valve simultaneously.
Other advantage of some embodiment of the utility model is that it provides a kind of priority valve, and threshold values hold-off pressure wherein can outsidely be regulated the adjusting of the threshold values hold-off pressure that carries out any requirement and relatively be easy to and realize.
Description of drawings
In conjunction with the drawings with reference to the following description of the utility model embodiment, above-mentioned becoming apparent simultaneously with further feature of the present utility model will better be understood the utility model self, wherein:
Fig. 1 is the schematic views according to hydraulic efficiency pressure system of the present utility model.
Fig. 2 is the cross-sectional scheme drawing of the part of the priority valve under the proper flow state.
Fig. 3 is the cross-sectional schematic views of part of the priority valve of Fig. 2, and wherein the pressure of brake boost has reached control presssure and causes traffic steering to the steering gear work-saving device.
Run through the corresponding reference letter of a few width of cloth views and indicate corresponding part.Though the embodiment of simplified illustration a kind of pattern of the present utility model of She Dinging herein, following public embodiment do not plan maybe will constitute completely to limit scope of the present utility model to disclosed accurate form.
The specific embodiment
Fig. 1 represents that the hydraulic efficiency pressure system 10 of vehicle 12 is used for the power-assisted of Vehicular turn and system fortune.This hydraulic efficiency pressure system comprises Hydraulic Pump 14 and fuel tank 16.As directed, this fuel tank can comprise in the pump 14 or can be positioned at apart from pump 14 slightly at a distance.
This pump 14 is transported to flow flow divider valve 20 through outfall pipeline 18 with high-voltage hydraulic fluid and is also referred to as priority valve.This priority valve 20, is communicated with the first hydraulic applications device 22, the second hydraulic applications device 24 and fuel tank 16 the predetermined work state of system 10 of explanation successively selectively according to below.
This first and second hydraulic applications device 22,24 is got the form in hydraulic efficiency gear or hydraulic subsidiary loop.In an illustrated embodiment, first application apparatus 22 is hydraulic braking force aid system or booster device and second application apparatus 24 is fluid-link steering gear force aid system or device.
The drg 28 of this hydraulic braking booster device 22 and main oil cylinder 26 and brake system also further is communicated with power steering device 24 by pipeline 25.Shown in the system 10, hydraulic braking work-saving device 22 and fluid-link steering gear work-saving device 24 have hold-off pressure, they are equivalent basically.
With reference to Fig. 2 and 3, this priority valve 20 comprises the valve body 30 with the hole that constitutes valve pocket 32, holds slidably FLOW CONTROL valve member 34 in this chamber.In valve body 30, be provided with some mouthfuls, and be expressed as port A (ingress port), B (outlet port), C (bypass ports) and D (low-pressure port) in the drawings.Come the fluid of self-pumping 14 to be incorporated in the valve body 30 through ingress port A, it enters valve pocket 32 and according to the mode of operation that will introduce now at this place, through one or several exits port B, C and D draw valve body 30.
Fig. 2 represents that priority valve 20 is from the back pressure of brake booster 22 with from the normal operation of back pressure under the state below the expectant control pressure of power steering device 24.Whole flows of inlet port port A through the main flow channel of valve 20 by and deliver to hydraulic braking servo-unit 22 through port B as prescribed route.
In proper flow state shown in Figure 2, brake servo unit 22 and steering booster 24 the two while fluid of working in predetermined threshold value or below the hold-off pressure freely flow to port A and flow export port B through main flow channel 35.As directed, valve body 30 can assemble connection fittings 36 that extend in the valve pocket 32.
Elongated valve pocket 32 has along axis 33 and first column part, 46 coaxillay aligned two column parts, and this first column part has the diameter bigger than second column part 48.In an illustrated embodiment, connection fittings 36 comprise the screw thread 58 that combines with cooresponding screw thread in the big column part 46 of valve pocket 32 and leak free O type ring 60 are provided.Connection fittings 36 also comprise hollow tubular portion 50, have the open end 52 that extends in the valve pocket 32.Tubular portion 50 has than the less overall diameter of the interior diameter of the column part 46 of valve pocket 32 thereby limit the space 56 of a centre between tube 50 and valve body 30 in valve pocket.Tubular portion 50 also comprises sidewall opening 54, and this opening provides fluid to be communicated with between the inside 37 of the space 56 of centre and connection fittings 36.Ingress port A and middle space 56 are that fluid is communicated with and exports port B is that fluid is communicated with the inside 37 of accessory 36.Therefore, in the embodiment shown, by the internal capacity of space 56, sidewall opening 54 and the accessory 36 of centre limit main flow channel 35 footpath valves 20 from port A to port B.
The back volume 44 that is positioned at the valve opening 32 of valve member 34 back is the pressure that is in the pressure of corresponding fuel tank 16, this fuel tank through port D with after volume 44 be communicated with.In the embodiment shown, fuel tank 16 is arranged on the upstream of the downstream of steering gear 24 and pump 14 and keeps hydraulic fluid to be in lower pressure.Valve member 34 separates low pressure volume 44 hermetically and separates and prevent the transfer of the fluid between main thoroughfare 35 and the low-voltage space 44 in the head seal ground of valve member 34 simultaneously with valve pocket 32 between the main thoroughfare 35 that port B fluid is communicated with.Fluid pressure in the back volume 44 is close to connection fittings 36 forward with the bias force hold-off valve 34 under the proper flow state by 42 effects of FLOW CONTROL spring.Position herein, as shown in Figure 2, this valve 34 sealed port C are not communicated with valve pocket 32 fluids and prevent that fluid from entering through bypass ports C, D through port A that any leaves.Therefore, when valve 34 is in position shown in Figure 2, whole fluids of inlet port port A through port B discharging simultaneously fluid both entered or discharged without any one of port C or D.Certainly, for all actual device, because there is some intrinsic fluid loss in the gap between each part.
Referring now to Fig. 3, pressure and main thoroughfare 35 that expression is set up in port B by brake booster 22 surpass the predetermined state that faces Jie's force value or control presssure.(hydraulic fluid when valve member 34 is in position shown in Figure 2 in the main thoroughfare 35 is subjected to the influence of valve member 34 through the open end of connection fittings 36).This threshold value is determined by the fluid pressure in the back volume 44 and the combination of the bias force that is acted on by spring 42.This threshold pressure preferably sets just below the hold-off pressure of pump 14.When the back pressure in the main thoroughfare 35 during near predetermined threshold value pressure, affact pressure on the valve 34 valve 34 axially slide backed be close to 42 whiles of spring afterwards the fluid pressure in the volumes 44 from first axial location shown in Fig. 2 to second axial location shown in Figure 3, the open end 52 of it and tubular portion 50 separates at this place.In position shown in Figure 3, valve 34 footpath slides backward bypass ports C is exposed to the main flow of the fluid of coming in through port A of being discharged by pump.Therefore through port A come the flow of self-pumping 14 be advanced to port B and port C the two, be delivered directly to power steering device 24 through port C, bypass brake booster 22 with the overwhelming majority of flow.Therefore, flow control valve member 34 work is flowed and is elevated to more than the predetermined threshold value pressure with the line pressure that prevents brake booster 22 automatically to measure excessive oil through gear bypass ports C, as mentioned above, threshold pressure preferably sets just below the hold-off pressure of pump 14.
Valve 20 provides flow separation or priority valve to have fairly simple and structure that be easy to make to have the fluid communication channels that elongated valve pocket 32, ingress port A, outlet port B, bypass ports C and low-pressure port D are the special uses that limited by valve 20.In the embodiment shown, elongated as mentioned above valve pocket 32 has the column part 46,48 of two different-diameters.Valve member 34 is placed in has the main flow channel 35 that extends through than major diameter part 46 in the smaller diameter portion 48.Port C and D are communicated with smaller diameter portion 46 fluids with being communicated with than major diameter part 48 fluids for port A and B.
In another embodiment, it is contemplated that port D may be influenced by ambient pressure thereby control presssure will not depend on pressure in the fuel tank 16.In this another embodiment, use is positioned at sealing member on the valve member 34 to prevent the leakage of hydraulic fluid.Also can use around being arranged in and the additional encryption sealing between the valve member 34 with the leakage that prevents hydraulic fluid with pollute the two.
Valve 20 also comprises screw thread stopper 40, and it operationally combines with biasing member 42.In the embodiment shown, as can seeing in Fig. 2 and 3, biasing member 42 is for being the screw thread stopper with the helical spring form of valve member 34 combinations at its relative end at one end.But stopper 40 has the stopper 40 of the axial location screw while green phase that combines with the screw thread of the common running that forms can be regulated to(for) valve body 30 rotation stoppers 40 in valve opening 32.The use of screw thread stopper allows to pass through simply valve body 30 rotation stoppers 40 adjusting after priority valve 20 assemblings relatively by the bias force that spring 42 acts on the valve member 34.Require adjusting after priority valve 20 is installed if at first expose port C at this place's valve member so that fluid flows to the control presssure valve of bypass brake booster 22 from pump 14, then screw thread stopper 40 makes this adjusting extremely easy.Another of priority valve be embodiment wherein stopper be press fitted in the valve body 30 and cannot regulate from the outside simultaneously or valve body 30 be provided with blind hole, but these also are in the scope of the present utility model.
If the pressure after port C has exposed in the main thoroughfare 35 continues to rise, then valve member 34 will continue to slide backward in valve opening 32.May design valve opening 32, port D and valve member 34 but then, like this port D final because this lasting rising of pressure is exposed and thereby allow to enter priority valve 20 so that be discharged through port A through the two bypass of port D and brake booster 22 and steering gear work-saving device 24 from the part of pump 14 fluid discharged flows, shown in the structure of priority valve 20 do not allow valve member 34 to expose port D.
Very clear from above description, hydraulic circuit 10 comprises, arranges and series sequence Hydraulic Pump 14, valve 20, brake booster device 22, steering transmission linkage 24 and fuel tank 16 with series connection.When valve 20 not with the part of fluid flow when port C redirect to bypass brake booster device 22, as what when brake servo unit 22 produces higher back pressure, occur, the main flow passage 11 that will extend along outlet port from sizable part of pump 14 fluid discharged flows from pump 14, through outfall pipeline 18, through valve 20 along main flow channel 35 from port A to port B, flow to brake servo unit 22 through hydraulic power line 19, arrive steering gear 24 through hydraulic power line 25, arrive fuel tank 16 through hydraulic power line 27, arrive the ingress port of pump 14 then, wherein repeat this circulation.As mentioned above, when the pressure of brake servo unit 22 upstreams is elevated to threshold value, valve 20 is with the separation of the fluid flow, with a part be communicated to braking help in the main flow passage of device 22 upstreams port B simultaneously another part of fluid flow redirect to hydraulic power line 21 through bypass ports C, this pipeline fluid is communicated in the main flow passage of upstream of the downstream of brake servo unit 22 and steering transmission linkage 24 a bit.
Although above hydraulic efficiency pressure system with reference to steering gear work-saving device and the two combination of brake booster has been described the utility model, it also can use other hydraulic efficiency gear and system.For example, known use single fluid pump drives the fluid motor and second fluid motor relevant with the radiator cooling fan of power steering device.For example, US Patent NO.5802848 disclose have the steering gear work-saving device and have the fluid motor that drives by single hydraulic fluid pump the radiator cooling fan system and by with reference to being included in wherein.In another embodiment of the present utility model, wherein disclosed priority valve can be used for using single hydraulic fluid pump with the two fluid motor of the device that drives steering gear work-saving device and heat radiation cooling fan with facility.
In addition, the priority valve that can use native system with control and two hydraulic efficiency gear (for example, brake booster, steering gear work-saving device, radiator fan or other hydraulic efficiency gear with fluid motor) or the fluid flow of two hydraulic circuit associated, the wherein hydraulic efficiency gear or the loop of priority valve and two associated constitute the part in bigger complicated hydraulic loop.
Have exemplary design although the utility model is described as, the spirit and scope that the utility model holds within it can further be revised with interior.Therefore should be with attempting to use its general principle to contain any variation of the utility model, application or comformability.
Claims (18)
1, a kind of automobile hydraulic system is characterized in that, comprising:
Hydraulic circuit, having series sequence that series connection is arranged and the main flow passage in edge is Hydraulic Pump, the first hydraulic applications device and the second hydraulic applications device; Simultaneously
Wherein said hydraulic circuit also comprises the valve with valve body and valve member; Described valve body limits an elongated valve pocket that is limited with an axis, and wherein said valve member axially is slidably disposed in the described chamber between first axial location and second axial location and hermetically the separation of described chamber is split into main flow channel and low-voltage space; Described valve body also limits the ingress port that is communicated with described main flow channel fluid, the outlet port that is communicated with described main flow channel fluid, the low-pressure port and the bypass ports that are communicated with described low-voltage space fluid, described bypass ports is arranged on axial midway location and is arranged on the side of described bypass ports with described low-pressure port, described ingress port is arranged on the axial side relative with described bypass ports with described outlet port, described bypass ports is not sealed to and is communicated with described valve pocket fluid when described valve member is in described first axial location, described bypass ports is communicated with described main flow channel fluid when described valve member is in described second axial location, when the fluid pressure in the described main flow channel is elevated to threshold value described valve member from described primary shaft to position axis to being displaced to second axial location, wherein said elongated valve pocket simultaneously, described ingress port, described outlet port, described bypass ports and described low-pressure port are the unique fluid communication channels that is limited by described valve; And wherein
Described valve is arranged on operationally that wherein said main flow passage extends to described ingress port from described Hydraulic Pump in the described hydraulic circuit of described pump downstream and the described first hydraulic applications device upstream, through the described outlet port of described main flow channel and described valve to described first hydraulic applications device operation; Described bypass ports and described main flow passage in the downstream of the described first hydraulic applications device and the fluid of a bit locating of the upstream of the described second hydraulic applications device be communicated with.
2, the automobile hydraulic system of claim 1, it is characterized in that, wherein said valve also is included in the connection fittings that one of described ingress port and outlet port locate to be fixed to described valve, described connection fittings qualification runs through flow channel wherein and extend in the described main flow channel, described valve member combines with described connection fittings when described valve member is in described first axial location, and described valve member and described connection fittings axially separate when described valve member is in described second axial location.
3, the automobile hydraulic system of claim 1 is characterized in that, comprises that also the while is towards the biasing member of the described valve member of the described first axial location bias voltage in the described low-voltage space that is arranged on described valve.
4, the automobile hydraulic system of claim 3, it is characterized in that, wherein said valve also comprises the screw member that operationally combines with described biasing member, and described screw member can axially relocate outside, and described threshold value is regulated in axially relocating of wherein said screw member.
5, the automobile hydraulic system of claim 1 is characterized in that, also comprises the hydraulic reservoir that is arranged on described second hydraulic applications device downstream and described pump upstream, and described low-pressure port is communicated with described hydraulic reservoir fluid.
6, the automobile hydraulic system of claim 1, it is characterized in that, wherein said valve pocket comprises the first basic cylinder partial sum second basic column part, and wherein said first and second column parts are provided with simultaneously described first column part coaxially and limit than the bigger diameter of second column part; Described ingress port and described outlet port are communicated with the described first column part fluid, and described low-pressure port and described bypass ports are communicated with the described second column part fluid;
Be arranged on described ingress port and the outlet port first in connection fittings, described connection fittings limit the fluid passage of running through wherein, and having hollow tubular partly to have a unlimited end extend in described first column part, at least one sidewall opening provides described fluid passage to be communicated with fluid between the intermediate space in described tubular portion, between described tubular portion and described first column part, limit this intermediate space, described ingress port and outlet second of port are communicated with described intermediate space fluid, described valve member combines with the described open end of described tubular portion and expose fluid in described fluid passage when described valve member is in first axial location, described valve member when it is in described second axial location and the open end of described tubular portion axially separate.
7, the automobile hydraulic system of claim 6 is characterized in that, also comprises being arranged on being biased into the biasing member that combines with described connection fittings in described second column part and with described valve member.
8, the automobile hydraulic system of claim 7, it is characterized in that, wherein said valve also comprises the screw member of the close described second column part end that combines with described valve body, operationally combine simultaneously with described biasing member, described screw member can axially relocate outside, and described threshold value is regulated in axially relocating of wherein said screw member.
9, the automobile hydraulic system of claim 1 is characterized in that, the wherein said first hydraulic applications device is the hydraulic braking booster device.
10, the automobile hydraulic system of claim 1 is characterized in that, the wherein said second hydraulic applications device is the fluid-link steering driving device.
11, a kind of automobile hydraulic system is characterized in that, comprising:
Hydraulic circuit, having series sequence that series connection is arranged and the main flow passage in edge is Hydraulic Pump, hydraulic braking booster device and fluid-link steering driving device; And
Wherein said hydraulic circuit also comprises the valve with valve body and valve member, described valve body limits an elongated valve pocket that limits an axis, wherein said valve member axially movably is arranged in the described valve pocket between first axial location and second axial location, hermetically described chamber is separated into main flow channel and low-voltage space simultaneously; Described valve body also limits the ingress port that is communicated with described main flow channel fluid; The outlet port that is communicated with described main flow channel fluid; The low-pressure port and the bypass ports that are communicated with described low-voltage space fluid, described bypass ports is arranged on that axial midway location is arranged on a side of described bypass ports with described low-pressure port and described ingress port and described outlet port are arranged on a relative axial side of described bypass ports, described bypass ports is sealed when described valve member is in first axial location is not communicated with the valve pocket fluid simultaneously that described bypass ports is communicated with described main flow channel fluid when described valve member is in second axial location, described valve member is displaced to described second axial location to position axis to ground from described primary shaft when the flow pressure in the described main flow channel is elevated to threshold value, simultaneously wherein said elongated valve pocket, described ingress port, described outlet port, described bypass ports and described low-pressure port are the unique fluid communication channels that is limited by described valve; And wherein
Described valve operationally is arranged in the described hydraulic circuit of described pump downstream and described brake booster device upstream, wherein said main flow passage extends to described ingress port from described Hydraulic Pump, and the outlet port of described main flow passage of process and described valve is to described brake booster device; Described bypass ports is communicated with the fluid of a bit locating of described main flow passage in described brake booster device downstream and described steering transmission linkage upstream.
12, the automobile hydraulic system of claim 11, it is characterized in that, wherein said valve also is included in the connection fittings that one of described ingress port and outlet port locate to be fixed to described valve, described connection fittings qualification runs through a fluid passage wherein and extend in the described main flow channel, described valve member combines with described connection fittings when described valve member is in described first axial location, and described valve member and described connection fittings axially separate when described valve member is in described second axial location.
13, the automobile hydraulic system of claim 11 is characterized in that, also comprises the biasing member that the described valve member of while bias voltage combines with described connection fittings in the institute's art low-voltage space that is arranged on described valve.
14, the automobile hydraulic system of claim 13, it is characterized in that, wherein said valve also comprises the screw member that operationally combines with described biasing member, and described screw member can axially relocate outside, and described threshold value is regulated in axially relocating of wherein said screw member.
15, the automobile hydraulic system of claim 11 is characterized in that, also comprises the hydraulic reservoir that is arranged on described steering transmission linkage downstream and described pump upstream, and described low-pressure port is communicated with described hydraulic reservoir fluid ground.
16, the automobile hydraulic system of claim 11, it is characterized in that, wherein said valve pocket comprises the first basic cylinder partial sum second basic column part, and wherein said first and second column part is provided with coaxially, and simultaneously described first column part limits than the bigger diameter of second column part; Described ingress port and described outlet port are communicated with the described first column part fluid ground, and described low-pressure port and described bypass ports are communicated with the described second column part fluid ground;
Be arranged on described ingress port and the outlet port first on connection fittings, described connection fittings limit the fluid passage of running through wherein, having hollow tubular portion simultaneously has open end and extend in described first column part, at least one sidewall opening in described tubular portion provides fluid to be communicated with between described fluid passage and intermediate space, this intermediate space limits between described tubular portion and described first column part, second of described ingress port and outlet port is that fluid ground is communicated with described intermediate space, described valve member combines with the open end of described tubular portion and exposes fluid in described fluid passage when described valve member is in described first axial location, and the open end of described valve member and described tubular portion axially separates when described valve member is in described second axial location.
17, claim 16 automobile hydraulic system, it is characterized in that, also comprise being arranged in second column part biasing member that the described valve member of bias voltage simultaneously combines with described connection fittings.
18, the automobile hydraulic system of claim 17, it is characterized in that, wherein said valve also comprises also operationally combining with described biasing member near the screw member of stating second column part of combining with described valve body, described screw member is can axially relocate outside, and described threshold value is regulated in axially relocating of wherein said screw member.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US11/901,822 US7779744B2 (en) | 2006-09-20 | 2007-09-19 | Vehicular hydraulic system with priority valve |
| US11/901822 | 2007-09-19 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201231748Y true CN201231748Y (en) | 2009-05-06 |
Family
ID=40618126
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008200094992U Expired - Fee Related CN201231748Y (en) | 2007-09-19 | 2008-04-29 | Vehicle hydraulic system with priority valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201231748Y (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106996404A (en) * | 2016-01-26 | 2017-08-01 | 迪尔公司 | Recessed installing type inserting hydraulic pump and the working truck transmission system with it |
| CN109424596A (en) * | 2017-08-28 | 2019-03-05 | 中国石油天然气股份有限公司 | A kind of sequence valve |
| CN112368193A (en) * | 2018-07-11 | 2021-02-12 | 罗伯特·博世有限公司 | Hydraulic control unit for vehicle brake system |
| CN112752662A (en) * | 2020-12-30 | 2021-05-04 | 华为技术有限公司 | Integrated suspension and brake system |
-
2008
- 2008-04-29 CN CNU2008200094992U patent/CN201231748Y/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106996404A (en) * | 2016-01-26 | 2017-08-01 | 迪尔公司 | Recessed installing type inserting hydraulic pump and the working truck transmission system with it |
| CN106996404B (en) * | 2016-01-26 | 2020-06-23 | 迪尔公司 | Recessed installation formula cartridge hydraulic pump and have its work vehicle transmission system |
| US10919376B2 (en) | 2016-01-26 | 2021-02-16 | Deere & Company | Recess-mounted hydraulic pump cartridge and work vehicle drivetrain therewith |
| CN109424596A (en) * | 2017-08-28 | 2019-03-05 | 中国石油天然气股份有限公司 | A kind of sequence valve |
| CN109424596B (en) * | 2017-08-28 | 2023-09-26 | 中国石油天然气股份有限公司 | Sequence valve |
| CN112368193A (en) * | 2018-07-11 | 2021-02-12 | 罗伯特·博世有限公司 | Hydraulic control unit for vehicle brake system |
| CN112368193B (en) * | 2018-07-11 | 2023-04-18 | 罗伯特·博世有限公司 | Hydraulic control unit for vehicle brake system |
| CN112752662A (en) * | 2020-12-30 | 2021-05-04 | 华为技术有限公司 | Integrated suspension and brake system |
| WO2022141264A1 (en) * | 2020-12-30 | 2022-07-07 | 华为技术有限公司 | Integrated suspension and braking system |
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