CN201280127Y - Hydraulic system with pressure release and relief valve apparatus for automobile - Google Patents
Hydraulic system with pressure release and relief valve apparatus for automobile Download PDFInfo
- Publication number
- CN201280127Y CN201280127Y CNU2008200094988U CN200820009498U CN201280127Y CN 201280127 Y CN201280127 Y CN 201280127Y CN U2008200094988 U CNU2008200094988 U CN U2008200094988U CN 200820009498 U CN200820009498 U CN 200820009498U CN 201280127 Y CN201280127 Y CN 201280127Y
- Authority
- CN
- China
- Prior art keywords
- valve
- fluid
- hydraulic
- pressure
- bringing device
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
A vehicle hydraulic system with a pressure relief valve device comprises a pump, a first application device, a pressure relief valve and a second application device, which are serially connected with each other. When the pressure exceeds a threshold, the pressure relief valve guides a portion of a primary fluid flow to pass through the second application device. A valve component in the pressure relief valve defines a pressure relief hole, which allows the fluid to pass through the valve component. When the pressure in the valve is lower than the threshold, a check valve is enabled to prevent the fluid from passing through the pressure relief hole. When the pressure exceeds the threshold, the fluid passes through the check valve and the pressure relief hole, thereby resulting in the movement of the valve component to expose a bypass hole. Accordingly, a portion of the primary fluid flow turns to the second application device. The check valve is selectively variable to adjust the threshold. A pressure sequence valve is also arranged on the upstream side of the first application device.
Description
Technical field
The utility model relates to the hydraulic efficiency pressure system that is used for vehicle, and more particularly, the utility model relates to a kind of hydraulic efficiency pressure system with hydraulic fluid pump and at least one hydraulic pressure bringing device.
Background technology
Many trucies with hydraulic brake system, particularly relatively large petrol power truck and diesel truck all include the hydraulic braking ancillary system, rather than common vacuum-assisted system in the passenger car.Sink and use the vacuum-assisted brake system to have problems in the vehicle of blow-fed engine and these vehicles also will adopt the hydraulic braking ancillary system usually having the whirlpool.In addition, for being used for the hydraulic braking ancillary system of high speed horsepower automobile of vehicle such as used car repacking, also there is the after market demand, these vehicles otherwise may not have brake auxiliary device or for this vehicle, use the vacuum-assisted system to have difficulties.This hydraulic braking ancillary system is well-known and is commercial on sale.
Generally, thus these hydraulic braking ancillary systems are connected in series between steering gear and Hydraulic Pump and are used to produce necessary pressure from the stream of this pump and provide braking auxiliary as required.Come the circulation of self-pumping often to be limited in the narrower flow rates and do not change to satisfy the travel condition of vehicle that changes on one's own initiative.Because this install in series, therefore braking apply and the joint of hydraulic braking ancillary system can influence the flow of hydraulic fluid that flows to steering gear, influence the obtainable auxiliary quantity of steering gear thus.Especially, when applying recasting during live load, this has caused improving the back pressure of pump, the back pressure of raising can exceed pump the threshold value relieving pressure (for example 1,500psi).More than the level, pump bypass is opened the inlet port that arrives pump so that the part of effluent is gone back at this, proceeds in this inlet port place circulation, is reduced to until the pressure from brake auxiliary device below the threshold value of bypass disc.Under this its deflated state, the fluid stream of minimizing is transferred into steering gear, thereby this effort that turns to that can cause vehicle operators to do produces the increase steering wheel rotation under extreme its deflated state that can aware.
In order to alleviate this state at least in part, diverter or priority valve might be placed hydraulic efficiency pressure system so that under the moving state of recasting, make the part of the fluid stream of discharging from pump be diverted to steering gear.U.S. Patent No. 6,814, the disclosure content of 413 B2 have been described the application of this diverter and thereby have been cited as a reference at this.Although a part of utilizing diverter to be flowed by the fluid that pump is discharged under the moving state of recasting is diverted to the way of steering gear auxiliary device significant advantage is provided, utilize this diverter need make the steering gear device have the same at least big pressure releasing value of pressure releasing value with brake auxiliary device usually.
Generally, the steering gear auxiliary device that is applicable to particular vehicle will have the lower pressure releasing value of the brake auxiliary device more required than this same vehicle.Therefore, this needs of steering gear auxiliary device with the same at least big pressure releasing value of pressure releasing value with brake auxiliary device have produced direct influence and can cause selecting more expensive steering gear auxiliary device the selection of steering gear auxiliary device usually.
The utility model content
The utility model provides a kind of pressure release and discharge-service valve device of pressure of the entrance that can be used to limit the hydraulic pressure bringing device in the automobile-used hydraulic efficiency pressure system.
A kind of form of the present utility model comprises a kind of automobile-used hydraulic efficiency pressure system with hydraulic circuit, and described hydraulic circuit has by install in series and the Hydraulic Pump that is set up in order along elementary flow path, pressure relief valve and hydraulic pressure bringing device.Described pressure relief valve has valve body and valve member.Described valve body limits the valve chamber with axis.Described valve member can indoorly slide vertically between first axial location and second axial location and described chamber is separated into elementary flow channel and secondary volumetric spaces described.Described valve member also limits the decompression aperture, and described decompression aperture provides fluid to be communicated with between described elementary flow channel and described secondary volumetric spaces.Secondary volumetric spaces hole and by-pass prot that described valve body limits the ingate that is communicated with described elementary flow channel fluid, the egress hole that is communicated with described elementary flow channel fluid, is communicated with described secondary volumetric spaces fluid.Described by-pass prot is set at axial midway location place, and described secondary volumetric spaces hole is set on the axial sidepiece of described by-pass prot and described ingate is set on the relative axial sidepiece of described by-pass prot with described egress hole.When described valve member was in described first axial positions, described by-pass prot was sealed so that be not communicated with described valve chamber fluid.When described valve member was in described second axial positions, described by-pass prot was communicated with described elementary flow channel fluid.Described pressure relief valve operationally is arranged in the described hydraulic circuit, and wherein said elementary flow path extends to described ingate, arrives the second hydraulic pressure bringing device by described elementary flow channel and described egress hole.Described by-pass prot is communicated with described elementary mobile path flow body at the some place that is positioned at described hydraulic pressure bringing device downstream and is positioned at described pump upstream.Biasing member operationally connects with described valve member and described valve member is setovered towards described primary importance.One way stop peturn valve operationally is being arranged in the described hydraulic circuit in described hydraulic pressure bringing device downstream and in the position of described pump upstream and between described secondary volumetric spaces hole and described elementary flow channel.When the pressure in the described elementary flow channel that is communicated to described secondary volumetric spaces by described decompression aperture surpassed threshold pressure value, described boiler check valve allowed fluid stream from described secondary volumetric spaces orifice flow to described elementary flow path.When described boiler check valve allows fluid flow to cross wherein, the fluid that flow to described secondary volumetric spaces from described elementary flow channel by described decompression aperture has experienced the reduction of pressure, make thus between described secondary volumetric spaces and described elementary flow channel, to have produced difference of pressure, the described valve member of described pressure official post from described primary shaft to location bias to described second axial location.When described closure of check ring and when having stopped fluid stream by wherein, described difference of pressure reduces and described biasing member makes the described valve member bias to described first axial location.
Embodiment more of the present utility model can have one way stop peturn valve, described one way stop peturn valve define for opening described boiler check valve so that fluid flow cross wherein for the resistance of selectively variable, it is adjustable making the described threshold pressure value that is limited by described boiler check valve thus.For more such selectively variable boiler check valve, can regulate described valve from the outside.
Other embodiment of the present utility model can comprise in described hydraulic circuit and priority valve or flow divider valve between described pump and the described first hydraulic pressure bringing device, wherein under first running state, all substantially described hydraulic fluids of discharging from described pump all cycle through described flow divider valve along described elementary flow path and arrive the described first hydraulic pressure bringing device.When the fluid of the described elementary flow path that is arranged in the described first hydraulic pressure bringing device upstream is increased to first threshold, described flow divider valve will be divided into second fluid stream of first fluid stream that is communicated to the described elementary flow path that is arranged in the described first hydraulic pressure bringing device upstream and the point that is communicated to the described elementary flow path that is positioned at the described first hydraulic pressure bringing device downstream and is positioned at described pressure relief valve upstream by the described hydraulic fluid that described pump is discharged.In other embodiments, the described first threshold that is limited by described flow divider valve is greater than the threshold value that is limited by described pressure relief valve.
In other embodiment of the present utility model, the described first hydraulic pressure bringing device can be taked the form of hydraulic braking booster device and the form that the described second hydraulic pressure bringing device can be taked the fluid-link steering wheel word.
Description of drawings
By the following description that embodiment of the present utility model is made and will be easier to understand above-mentioned feature of the present utility model and further feature in conjunction with the accompanying drawings and realize the mode of these features and will understand the utility model itself better, wherein:
Fig. 1 is the scheme drawing according to hydraulic efficiency pressure system of the present utility model;
Fig. 2 is the cutaway drawing of the priority valve under the normal flow state;
Fig. 3 is the cutaway drawing of priority valve shown in Figure 2, and wherein said priority valve just makes the part of described fluid stream turn to by hole C;
Fig. 4 is the pressure release under the low pressure state and the part cross-sectional schematic of discharge-service valve device; With
Fig. 5 is the part cross-sectional schematic of the valve gear shown in Figure 4 under high-pressure state.
Corresponding Reference numeral is represented corresponding parts in each all figure.Although the illustration that this paper makes shows a kind of form of an embodiment of the present utility model, following disclosed embodiment is not intended to have exhaustive or is regarded as scope of the present utility model is limited to disclosed particular form.
The specific embodiment
Fig. 1 shows with helping the hydraulic efficiency pressure system that is used for vehicle 12 10 that vehicle turns to and brakes.Described hydraulic efficiency pressure system comprises Hydraulic Pump 14 and storage facility 16.This storage facility can be included in the pump 14, as shown in FIG., maybe can be set at the position away from described pump 14.
Pump 14 is carried high pressure hydraulic fluid by downstream line 18 and is arrived flow divider valve 20, and described flow divider valve also is known as priority valve.This priority valve 20 and then according to the predetermined running state of system 10 and optionally be communicated with the first hydraulic pressure bringing device 22, the second hydraulic pressure bringing device 24 and storage facility 16, as following will be explanatorily.
The first hydraulic pressure bringing device 22 and the second hydraulic pressure bringing device 24 are taked the form in hydraulic efficiency gear or hydraulic subsidiary loop.In shown embodiment, first bringing device 22 is hydraulic braking ancillary system or booster device, and second bringing device 24 is fluid-link steering gear ancillary system or device.
Hydraulic braking auxiliary device 22 is communicated with the drg 28 of master cylinder 26 and brake system.The type that hydraulic booster apparatus 22 is had is well-known in the art, be set between the hydraulic main cylinder of Hydraulic Pump and automobile-used hydraulic brake system to described hydraulic booster apparatus one row formula, the effect of described hydraulic booster apparatus is to improve or amplify the power that is applied on the brake system, has alleviated that the brake pedal of making for brake activation is required is made great efforts and the required pedal travel that carries out thereby compare with the hand brake system.For example at United States Patent(USP) Nos. 4,620, disclosed this system in 750 and 4,967,643, the disclosure content of described US Patent all is cited as a reference and the example of suitable booster device 22 is provided at this.In brief, the hydraulic fluid from transfer pump 14 is communicated to booster device 22 by the servo-unit ingate and is conducted through the open centre cylindrical valve that can slide in servo-unit cavity (not shown).Power piston slides in contiguous cylinder and is exposed under the fluid pressure on the input side of piston and is attached to take-off lever on the opposite side.The input reaction bar that is connected to brake pedal extends in the housing and by input lever or connecting device and is attached to this cylindrical valve.The mobile cylindrical valve that makes of input bar moves, thereby fluid flow has produced restriction and the feasible pressure that is applied on the power piston that correspondingly improved.The steering pressure that is produced by steering gear ancillary system 24 is kept apart by cylindrical valve and servo-unit cavity and can not be influenced braking, has still produced for pump 14 really and has turned to auxiliary back pressure.Priority valve 20 turns round so that manage the flow of hydraulic fluid that flow to each ancillary system BAS (Brake Assist System) 22 and the steering assist system 24 from pump 14, so as to weaken steering swivel system and brake system aspect running to interdepending each other.
Referring to Fig. 2 and Fig. 3, priority valve 20 comprises valve body 30, and described valve body has the valve port that has formed chamber 32, and slidably flow control valve member 34 is accommodated in the described chamber.A plurality of holes are set in the valve body 30, and are marked as hole A, B, C and D in the drawings.Come the fluid of self-pumping 14 to be directed in the valve body 30 by hole A, state in the fluid inlet chamber 32 and in A place, described hole and to be drawn valve body 30, will be described described running state below by the one or more egress holes among egress hole B, C and the D according to running state.
Fig. 2 shows the normal operation that is lower than the priority valve 20 under the state of predetermined threshold or control presssure in the back pressure from brake auxiliary device 22.Primary channel 35 and as prescribed route that all stream that enters hole A all passes through the mouth 32 of diverter 20 arrive hydraulic braking servo-unit 22 by hole B.Certainly, for all actual device,, therefore can produce some fluid loss inherently owing between each parts, have clearance.
Under state as shown in Figure 2, brake servo unit 22 moves under the situation that is lower than predetermined threshold or relieving pressure value, and fluid freely also passes through passage 35 tap hole B in the ostium A.As shown in FIG., valve body 30 can be equipped with connection fittings 36, and described connection fittings extend in the valve port 32 and are formed with the primary channel 35 that is communicated with valve port 32 direct fluids.Line pressure in the primary channel 35 is communicated to the rear portion of flow control valve 34 by the communication paths 40 in the decompression in the connection fittings 36 or aperture, P hole (P-holeorifice) 38 and the valve body 30.This pressure remains against valve member 34 forward on the connection fittings 36 with the bias voltage that is applied by control stray bullet spring 42.In this position, valve member 34 covers fully to lead to respectively and turns to by-pass prot C, the D of auxiliary device 24 and storage facility 16, does not also flow out this two holes thereby make stream neither enter these two holes.Valve member 34 has storage facility pressure communication groove 44, and no matter what kind of position valve member 34 is in, and described storage facility pressure communication groove all always is exposed to hole D and therefore is exposed under the storage facility pressure.This storage facility pressure is communicated to the inside of valve by opening 46.Little poppet valve 50 is separated the fluid that fluid under the line pressure and valve member 34 in-to-ins are under the storage facility pressure that is in of valve member 34 back.
Transfer now referring to Fig. 3, there is shown the state that the braking aux. pressure that is formed in hole B and primary channel 35 by brake auxiliary device 22 has exceeded the predetermined threshold pressure value of brake auxiliary device 22, described predetermined threshold pressure value preferably is configured to be lower than just the relieving pressure of pump 14.When the back pressure in the elementary passage 35 during near predetermined control pressure, the fluid pressure that is communicated to the rear side of flow control valve member 34 will cause the lifting ball 52 of poppet valve 50 to leave original position, and this will cause some hydraulic oil to be discharged in plunger 54 back of valve member 34 and be discharged from by opening in the valve member 34 46 and hole D arriving storage facility 16.Because aperture 38, P hole is quite little, therefore as long as poppet valve 50 is opened and make oil be discharged from plunger 54 back, then communication paths pressure 40 will be lower than the line pressure in the primary channel 35.This difference of pressure will cause plunger 54 to slide backward from position shown in Figure 2 leaning against spring 42 to arrive position shown in Figure 3, hole C is exposed to by what pump 14 was discharged pass through the main fluid stream that hole A enters.Therefore the stream that comes self-pumping 14 that enters by hole A will be supplied to hole B and hole C, and quite most stream has been walked around brake auxiliary device 22 and is discharged from and is transported to steering gear auxiliary device 24 by hydraulic power line 25 by hole C.When the back pressure that is produced by brake auxiliary device 22 is increased to when presetting control presssure, therefore flow control valve 34 turns round so that automatic gauge passes through the too much oil stream of hole C, mention the ground as top, describedly preset the relieving pressure that control presssure preferably is configured to be lower than just pump 14.
The utility model also can adopt has heteroid priority valve, makes the fluid that turns to walk around brake auxiliary device 22 and be transported to steering gear auxiliary device 24 thereby described priority valve turns to flow of hydraulic fluid.For example, (sequence number is No. to Wong etc. in the novel patent application of U.S. utility
11/901,821) in the priority valve with simplified construction that can be used to replace described priority valve 20 has been described, the exercise question of the novel patent application of described U.S. utility is to have the automobile-used hydraulic efficiency pressure system of priority valve and discharge-service valve and act on behalf of case number for DP-315726 and to have required in the sequence number of application on September 20th, 2006 be No.60/845,911 U.S. Provisional Application No.; And (sequence number is No. to Wong etc. in the novel patent application of U.S. utility
11/901,822) in the priority valve with simplified construction that can be used to replace described priority valve 20 has also been described, the exercise question of the novel patent application of described U.S. utility is to have the automobile-used hydraulic efficiency pressure system of priority valve and act on behalf of case number for DP-315727 and to have required in the sequence number of application on September 20th, 2006 be No.60/845,892 U.S. Provisional Application No., these two utility application have the applying date common with the application, and wherein these two utility model applications and two provisional application all be transferred to the application's cessionary and wherein each in these four utility models and the provisional application all obviously be cited as a reference at this.
Hydraulic efficiency pressure system 10 also comprises fluid control pressure Dump valve 120 and discharge-service valve 146, and described fluid control pressure Dump valve and discharge-service valve are arranged the maximum pressure that is transferred to the hydraulic fluid of steering gear auxiliary device 24 with restriction.Referring to Fig. 4 and Fig. 5, pressure relief valve 120 comprises valve body 130, and described valve body has the mouth that has formed valve chamber 132, and slidably flow control valve member 134 is accommodated in the described valve chamber.A plurality of holes are set in the valve body 130, and are marked as hole E (ingate), F (by-pass prot), G (egress hole) and H (secondary volumetric spaces hole) in the drawings.Be directed in the valve body 130 by ingate E from the outlet of brake auxiliary device 22 with from the fluid of the hole C of priority valve 20, state in the fluid inlet chamber 132 and in place, described ingate and, will be described described running state below by being drawn valve body 130 in the one or more holes among hole F, G and the H according to running state.
Fig. 4 shows the valve 120 under the low-pressure state that pressure in the entrance of steering gear auxiliary device 24 is lower than second predetermined threshold pressure.In the embodiment shown, the pressure at the pressure in the primary channel 135 and hole E and G place will be identical substantially with the pressure of the entrance of steering gear auxiliary device 24.Under state as shown in Figure 4, enter primary channel 135 and the as prescribed route that all streams of hole E all can through port 132 and arrive fluid-link steering gear auxiliary device by hole G.When on steering gear auxiliary device 24, not having obvious load, may there be this low-pressure state.
As shown in FIG., valve body 130 can be equipped with connection fittings 136, and described connection fittings extend in the valve chamber 132.Primary channel 135 extends through connection fittings 136.Elongated valve chamber 132 has two cylindrical portion sections of coaxially aliging along axis 133, and the first cylindrical portion section 147 has the diameter bigger than the second cylindrical portion section 149.In embodiment as shown in the figure, connection fittings 136 comprise that respective threads engages in the great circle cylindrical portion section 147 with valve chamber 132 screw thread 158 and O shape circle 160 are so that provide sealing.Connection fittings 136 also comprise hollow tubular part 151, and described hollow tubular partly has the open end 153 that extends in the valve chamber 132.Barrel portion 151 has the littler external diameter of internal diameter than the cylindrical portion section 147 of chamber 132, makes thus to limit clearance space 156 between barrel portion 151 and valve body 130 in valve chamber 132.Barrel portion 151 also comprises sidewall opening 154, and described sidewall opening provides fluid to be communicated with between the inside 137 of clearance space 156 and connection fittings 136.Ingate E is communicated with clearance space 156 fluids, and egress hole G is communicated with inside 137 fluids of accessory 136.Therefore, in the embodiment shown, limit from hole E by the elementary flow channel 135 of valve 120 to hole G by the inner space 137 of clearance space 156, sidewall opening 154 and accessory 136.
Valve member 134 comprises decompression aperture 138, and described decompression aperture provides fluid to be communicated with between primary channel 135 and secondary volumetric spaces 144 at the valve chamber 132 at the rear portion of valve member 134.Under low-pressure state as shown in Figure 4, secondary volumetric spaces 144 is communicated with hole H and 134 couples of hole F of valve member seal it is not communicated with valve chamber 132 fluids, thereby has both prevented from also to have prevented between hole F and the back volume space 144 that producing fluid between hole F and the primary channel 135 was communicated with.
Discharge-service valve 146 is set at the hydraulic power line 145 that extends to hydraulic power line 27 from secondary apertures H in the position that is arranged in steering gear device 24 downstreams and is positioned at pump 14 upstreams.Discharge-service valve 146 separates by the 145a of first and the hole H of pipeline 145, and the second portion 145b of pipeline 145 extends to pipeline 27 from valve 146.Discharge-service valve 146 has the ingate, hole I, and described ingate is communicated with hole H fluid by hydraulic power line part 45a.Discharge-service valve 146 has discharge orifice, hole J, and described discharge orifice is communicated with storage facility 16 by pipeline part 45b and pipeline 27.In the embodiment shown, storage facility 16 is set at steering gear 24 downstreams and pump 14 upstreams and hydraulic fluid is remained under the relatively low pressure.Fluid pressure in the hydraulic pressure storage facility 16 is communicated to discharge orifice J by fluid line 27 and 45b.Discharge-service valve 146 has prevented that fluid stream from flowing to hole I and allowing fluid stream to flow to hole J from hole I from hole J when the fluid pressure in the secondary volumetric spaces 144 has overcome the threshold pressure value of discharge-service valve 146, this will be explained in more detail below.
Under low-pressure state, discharge-service valve 146 is closed and has prevented that fluid stream from flowing to hole J from hole I.As mentioned above, secondary volumetric spaces 144 is communicated with primary channel 135 fluids by aperture 138.When discharge-service valve 146 be closed and fluid active Flow is not when the aperture 138, the pressure in the secondary volumetric spaces 144 will be identical with the fluid pressure in the primary channel 135.Therefore, under low-pressure state as shown in Figure 4, the fluid pressure in the secondary volumetric spaces 144 is identical with fluid pressure in the primary channel 135.Under these low-pressure states, the biasing member 142 that exists with helical spring form remains against valve member 134 forward on the connection fittings 136 in the embodiment shown.In this position, valve 134 prevents that the fluid that enters by hole E from leaving by by-pass prot F and arrives storage facility 16, and discharge-service valve 146 has prevented that fluid is discharged to storage facility 16 by hole H.Therefore, when valve 134 was in as shown in Figure 4 position, all fluids that enter hole E are discharged from by hole G and fluid neither enters also obstructed via hole F by hole F or H or H is discharged from.Certainly, for all actual device,, therefore can produce some fluid loss inherently owing between each parts, have clearance.
Transfer now to there is shown the high pressure its deflated state that the pressure that is formed by steering gear auxiliary device 24 has exceeded the threshold pressure value of discharge-service valve 146 in primary channel 135 and hole G and E referring to Fig. 5.(when valve member 134 was in as shown in Figure 4 axial positions, the hydraulic fluid in the primary channel 135 was exposed to valve member 134 by the open end 153 of connection fittings 136.) when the pressure in the elementary passage 135 during near threshold pressure, allow fluid flow to cross aperture 138, secondary volumetric spaces 144, hole H, fluid line 145a, hole I, discharge-service valve 146, hole J and fluid line 145b thereby this pressure increase causes discharge-service valve 146 to be opened.This fluid flow is crossed that fluid line 27 returns storage facility 16 and is by less relatively part in the total fluid stream of primary channel 135.When this fluid stream is opened and allowed to produce to discharge-service valve 146, fluid will experience differential pressure along with flowing through aperture 138.
When the back pressure that is produced at hole G place and in primary channel 135 by steering gear auxiliary device 24 drops to when making the degree that discharge-service valve 146 closes once more, the fluid stream by aperture 138 will be cut off and back volume space 144 in fluid pressure will equal fluid pressure in the primary channel 135.The result is, spring 142 will make valve member 134 biasing and cut off the fluid stream by hole F thus and make valve 120 return low-pressure state shown in Figure 4 forward once more.
The use of pressure relief valve 120 and discharge-service valve 146 makes it possible to use the steering gear device 24 with pressure releasing value littler than the pressure releasing value of brake auxiliary device 22.In the hydraulic circuit that comprises steering gear device with pressure releasing value littler than the pressure releasing value of brake auxiliary device, pressure relief valve 120 and discharge-service valve 146 will turn round so that prevent to surpass at the hydraulic fluid pressure of the entrance of steering gear auxiliary device 24 pressure limit value of steering gear auxiliary device 24, surpass the pressure limit value of brake auxiliary device 24 and priority valve 20 turns round so that prevent the hydraulic fluid pressure in the entrance of brake auxiliary device 22.Residing force value when making pressure relief valve 120 and discharge-service valve 146 at the entrance of steering gear auxiliary device 24 relieving pressure by making priority valve 20 residing force value when the relieving pressure of the entrance of brake auxiliary device 22 be arranged to be higher than, brake auxiliary device 22 can use with the steering gear auxiliary device in the hydraulic circuit 10 24, and wherein steering gear auxiliary device 24 has the pressure limit value lower than the pressure limit value of brake auxiliary device 22.
Should be noted that: although the valve chamber shown in the figure 132 is blind hole, in other optional embodiment, valve chamber 132 can be a through hole.For example, can form the end of the valve chamber 132 that engages with spring 142 by threaded plunger, described threaded plunger is adjustable vertically, can be by rotating threaded plunger and regulating its axial location with respect to valve port 132 and regulate the power that is applied by spring 142 thereby make thus.
In Fig. 4 and Fig. 5, discharge-service valve 146 is illustrated as the scalable discharge-service valve, yet in other optional embodiment of the present utility model, discharge-service valve 146 can be uncontrollable or adopt other optional form of scalable discharge-service valve.Fig. 5 shows the more schematic discharge-service valve 146 than Fig. 4.
Fig. 4 shows the structure of an embodiment of discharge-service valve 146.In the embodiment shown, valve 146 comprises air ball valve member 148, and the biasing member 150 that exists with helical spring form makes air ball valve member bias to off position.In Fig. 4, valve member 148 is positioned at the primary importance place, in this position, described valve member is closed valve 146 and is prevented that fluid flow from crossing wherein, and in Fig. 3, valve member 148 has been setovered and has been left its valve seat and arrive second open position, and this allows fluid flow to cross valve 46.Spring 150 operationally connects with threaded plunger 152 and makes first or the closed position of ball 148 towards as shown in Figure 4 described ball, and described operationally the connection is by spring 150 being engaged with plunger 152 realize on its end relative with ball 148.Plunger 152 has screw 162, and respective threads engages on the valve body of described screw and valve 146.Position by governing plunger 152, can regulate by spring 150 being applied to the biasing force on the ball 148 and therefore regulating and open the required fluid pressure of valve 146 from the outside, allow to regulate making residing control presssure when releasing fluid pressure thus in the entrance of steering gear auxiliary device 24 from the outside.In other words, valve 146 limits the resistance of selectively variable for opening valve 146, and the resistance of this selectively variable is the biasing force decision of difference of pressure between the fluid pressure of being located by fluid pressure of locating at hole E (ingate of valve 146) and hole F (discharge orifice of valve 146) and spring 150.By threaded plunger 152 is reorientated the biasing force that is applied by spring 150 is regulated and therefore also regulated the resistance of opening valve 146 and made valve 20 make fluid turn to residing threshold pressure by by-pass prot C.
In the description that provides from above clearly and distinctly, hydraulic circuit 10 comprises install in series and Hydraulic Pump 14, priority valve 20, brake booster device 22, pressure relief valve 120, steering gear device 24 and storage facility 16 that be provided with in order.When valve 20 does not make the part of fluid stream turn to walk around brake booster device 22 by hole C, when having produced higher relatively back pressure the what happens when brake servo unit 22, quite most of fluid streams from the fluid stream that pump 14 is discharged will flow along elementary flow path 11, and described elementary flow path extends from the outlet of pump 14, extend through downstream line 18, extend through valve 20 along elementary flow channel 35 from hole A and arrive hole B, arrive brake servo unit 22 and arrive pressure relief valve 120 by hydraulic power line 19 by hydraulic power line 125.When valve 120 does not discharge high-pressure fluid by hole F, when having produced higher relatively back pressure the what happens when steering gear device 24, quite most of fluid streams in the fluid stream in the pipeline 125 will continue to flow along elementary flow path 11, described elementary flow path further extends through valve 120 and arrives hole G, extends through the inlet that hydraulic power line 123 arrives steering gear 24, extends through the hydraulic power line 27 arrival storage facilities 16 and the pump 14 that arrives soon after along elementary flow channel 135 from hole E, circulating in described inlet repeats.As mentioned above, when the pressure of brake servo unit 22 upstreams is increased to first threshold, valve 20 will make the fluid stream division at valve 20 places, another part that the part of described fluid stream is communicated to hole B in the elementary flow path of brake servo unit 22 upstreams and fluid stream is diverted by by-pass prot C and arrives hydraulic power line 25, and described hydraulic power line makes fluid be communicated to being arranged in brake servo unit 22 downstreams and being positioned at the point of the elementary flow path of pressure relief valve 120 (with steering gear device 24) upstream in the hydraulic power line 125.Similarly, when the pressure of steering gear 24 upstreams is increased to second threshold value, valve 120 will make the fluid stream division at valve 120 places, and another part that the part of described fluid stream is communicated to hole G in the elementary flow path of steering gear 24 upstreams and fluid stream is diverted by by-pass prot F and arrives the point that is arranged in steering gear 24 downstreams and is positioned at the elementary flow path 11 of pump 14 upstreams.When valve 120 makes fluid turn to by by-pass prot F, relatively the fluid of small number also will flow through hole H, pipeline 145a, discharge-service valve 146, pipeline 145b arrives pipeline 27.
Although in conjunction with the hydraulic efficiency pressure system that steering gear auxiliary device and brake auxiliary device are combined the utility model is described above, the utility model also can be used for other hydraulic applications.For example, adopting single hydraulic fluid pump to come for the fluid motor that turns to auxiliary device and second fluid motor that is associated with the radiator cooling blower provide power is known way.For example, in U.S. Patent No. 5,802, disclosed a kind of system in 848 with steering gear auxiliary device and radiator cooling blower, described radiator cooling blower has the fluid motor that power is provided by single hydraulic fluid pump, and described US Patent is cited as a reference at this.In other optional embodiment of the present utility model, can adopt priority valve that this paper discloses and pressure release and discharge-service valve device so that help using single hydraulic fluid pump to come not only to provide power as the fluid motor of steering gear auxiliary device but also as the fluid motor of radiator cooling blower.
In addition, priority valve in the system of the present utility model and pressure release and discharge-service valve device can be used to the fluid that control is associated with two hydraulic efficiency gear (for example brake auxiliary device, steering gear auxiliary device, the radiator fan with fluid motor or other hydraulic efficiency gear) or two hydraulic circuits and flow, and wherein priority valve and pressure release and discharge-service valve device and two hydraulic efficiency gear that are associated or loop have formed the part in bigger complicated hydraulic loop.
In other embodiments, can not have under the situation of priority valve pressure release as herein described and discharge-service valve device to be used for hydraulic circuit.For example, in the hydraulic circuit that pressure release as herein described and discharge-service valve device can be used for integrating, the hydraulic circuit of described integration had not only had brake auxiliary device but also had had the steering gear auxiliary device but do not have priority valve.In this loop, pressure release and discharge-service valve device can make it possible to utilize steering gear auxiliary device with pressure releasing value lower than the pressure releasing value of brake auxiliary device or the steering gear auxiliary device of the pressure of the hydraulic fluid of releasing in the entrance of steering gear device simply when surpassing predetermined value.In addition, can adopt pressure release as herein described and discharge-service valve device at the conventional hydraulic circuit that is used for the steering gear auxiliary device, described conventional hydraulic circuit does not comprise that any other hydraulic efficiency gear limits the hydraulic fluid pressure of the entrance of steering gear auxiliary device.
Also pressure relief valve 120 and discharge-service valve 146 might be used for having and be arranged near the storage facility the pump 14 and be arranged near the valve 120,146 long-range storage facility or the hydraulic circuit of collection cryopreservation device.This way of utilizing two storage facilities not only is positioned at the storage pond of hydraulic fluid near pump 14 and the valve 120,146 but also can be used to increase the hydraulic fluid total amount in the hydraulic circuit and improve the heat absorption capacity of the hydraulic fluid in the loop thus.
Although the utility model has been described to have modular design, can in the spirit and scope of the utility model disclosure content, make further modification to the utility model.Therefore the application is intended to utilize its general principle to cover any modification of the present utility model, effectiveness or adaptive change.
Claims (20)
1, a kind of automobile-used hydraulic efficiency pressure system, described automobile-used hydraulic efficiency pressure system comprises hydraulic circuit, described hydraulic circuit has by install in series and the Hydraulic Pump and the hydraulic pressure bringing device that are set up in order along elementary flow path;
It is characterized in that,
Described hydraulic circuit further comprises and is set at the pressure relief valve between described Hydraulic Pump and described hydraulic pressure bringing device in the described elementary flow path, wherein said pressure relief valve comprises valve body and valve member, described valve body limits valve chamber, described valve chamber limits axis, wherein said valve member can indoorly slide vertically between first axial location and second axial location and described chamber is separated into elementary flow channel and secondary volumetric spaces described, described valve member further limits the decompression aperture, and described decompression aperture provides fluid to be communicated with between described elementary flow channel and described secondary volumetric spaces; Described valve body further limits the ingate that is communicated with described elementary flow channel fluid, the egress hole that is communicated with described elementary flow channel fluid, the secondary volumetric spaces hole that is communicated with described secondary volumetric spaces fluid, and by-pass prot, described by-pass prot is set at axial midway location place, and described secondary volumetric spaces hole is set on the axial sidepiece of described by-pass prot and described ingate is set on the relative axial sidepiece of described by-pass prot with described egress hole, when described valve member is in described first axial positions, described by-pass prot is sealed so that be not communicated with described valve chamber fluid, and when described valve member is in described second axial positions, described by-pass prot is communicated with described elementary flow channel fluid, described pressure relief valve operationally is arranged in the described hydraulic circuit, and wherein said elementary flow path extends to described ingate, arrive described hydraulic pressure bringing device by described elementary flow channel and described egress hole; Described by-pass prot is communicated with described elementary mobile path flow body at the some place that is positioned at described hydraulic pressure bringing device downstream and is positioned at described pump upstream;
Biasing member, described biasing member operationally connects with described valve member and described valve member is setovered towards described primary importance; With
One way stop peturn valve, described unidirectional non-return threshold operationally is being arranged in the described hydraulic circuit in described hydraulic pressure bringing device downstream and in the position of described pump upstream and between described secondary volumetric spaces hole and described elementary flow path; When the pressure in the described elementary flow channel that is communicated to described secondary volumetric spaces by described decompression aperture surpasses threshold pressure value, described boiler check valve allows fluid stream from described secondary volumetric spaces orifice flow to described elementary flow channel, and wherein when described boiler check valve allows fluid flow to cross wherein, the fluid that flow to described secondary volumetric spaces from described elementary flow channel by described decompression aperture has experienced the reduction of pressure, make thus between described secondary volumetric spaces and described elementary flow channel, to have produced difference of pressure, the described valve member of described pressure official post from described primary shaft to location bias to described second axial location; And wherein, when described closure of check ring and when having stopped fluid stream by wherein, described difference of pressure reduces and described biasing member makes the described valve member bias to described first axial location.
2, automobile-used hydraulic efficiency pressure system according to claim 1 is characterized in that, described hydraulic pressure bringing device is the fluid-link steering wheel word.
3, automobile-used hydraulic efficiency pressure system according to claim 1, it is characterized in that, described automobile-used hydraulic efficiency pressure system further comprises the first hydraulic pressure bringing device, and the described first hydraulic pressure bringing device operationally is arranged in the described hydraulic circuit and is positioned at described pump downstream and is positioned at described pressure relief valve upstream.
4, automobile-used hydraulic efficiency pressure system according to claim 1, it is characterized in that, described boiler check valve define for opening described boiler check valve so that fluid flow cross wherein for the resistance of selectively variable, it is adjustable making the described threshold pressure value that is limited by described boiler check valve thus.
5, automobile-used hydraulic efficiency pressure system according to claim 4 is characterized in that, the outside that described boiler check valve is carried out is regulated and optionally changed described resistance.
6, automobile-used hydraulic efficiency pressure system according to claim 1 is characterized in that, described one way stop peturn valve comprises:
Operationally be arranged in the described boiler check valve and second valve member that can between the primary importance and the second place, move, at described primary importance place, described second valve member prevents that fluid flow from crossing described boiler check valve, at described second place place, described second valve member allows fluid flow to cross described boiler check valve;
Make second biasing member of described second valve member towards described primary importance biasing; With
With the threaded member that described biasing member operationally connects, can reorientate from the outside to described threaded member, wherein reorientating of carrying out of described threaded member changed described threshold value.
7, automobile-used hydraulic efficiency pressure system according to claim 1, it is characterized in that, described automobile-used hydraulic efficiency pressure system further comprises and operationally is arranged in the described hydraulic circuit and is positioned at described hydraulic pressure bringing device downstream and is positioned at the hydraulic pressure storage facility of described pump upstream, and described one way stop peturn valve is communicated with described elementary flow channel fluid being positioned at the position that makes described by-pass prot be communicated with residing position upstream with described elementary flow channel fluid.
8, a kind of automobile-used hydraulic efficiency pressure system, described automobile-used hydraulic efficiency pressure system comprises hydraulic circuit, described hydraulic circuit has by install in series and the Hydraulic Pump that is set up in order along elementary flow path, flow divider valve, the first hydraulic pressure bringing device and the second hydraulic pressure bringing device;
It is characterized in that,
Described hydraulic circuit further comprises and is set at the pressure relief valve between described first hydraulic pressure bringing device and the described second hydraulic pressure bringing device in the described elementary flow path, wherein under first running state, all substantially described hydraulic fluids of discharging from described pump all cycle through described flow divider valve along described elementary flow path and arrive the described first hydraulic pressure bringing device; And when the fluid of the described elementary flow path that is arranged in the described first hydraulic pressure bringing device upstream is increased to first threshold, described flow divider valve will be divided into second fluid stream of first fluid stream that is communicated to the described elementary flow path that is arranged in the described first hydraulic pressure bringing device upstream and the point that is communicated to the described elementary flow path that is positioned at the described first hydraulic pressure bringing device downstream and is positioned at described pressure relief valve upstream by the described hydraulic fluid that described pump is discharged;
Wherein said pressure relief valve has valve body and valve member, described valve body limits valve chamber, described valve chamber limits axis, wherein said valve member can indoorly slide vertically between first axial location and second axial location and described chamber is separated into elementary flow channel and secondary volumetric spaces described, described valve member further limits the decompression aperture, and described decompression aperture provides fluid to be communicated with between described elementary flow channel and described secondary volumetric spaces; Described valve body further limits the ingate that is communicated with described elementary flow channel fluid, the egress hole that is communicated with described elementary flow channel fluid, the secondary volumetric spaces hole that is communicated with described secondary volumetric spaces fluid, and by-pass prot, described by-pass prot is set at axial midway location place, and described secondary volumetric spaces hole is set on the axial sidepiece of described by-pass prot and described ingate is set on the relative axial sidepiece of described by-pass prot with described egress hole, when described valve member is in described first axial positions, described by-pass prot is sealed so that be not communicated with described valve chamber fluid, and when described valve member is in described second axial positions, described by-pass prot is communicated with described elementary flow channel fluid, described pressure relief valve operationally is arranged in the described hydraulic circuit and is positioned at the described first hydraulic pressure bringing device downstream and is positioned at the described second hydraulic pressure bringing device upstream, and wherein said elementary flow path extends to described ingate from the described first hydraulic pressure bringing device, arrive the described second hydraulic pressure bringing device by described elementary flow channel and described egress hole; Described by-pass prot is communicated with described elementary mobile path flow body at the some place that is positioned at the described second hydraulic pressure bringing device downstream and is positioned at described pump upstream;
Biasing member, described biasing member operationally connects with described valve member and described valve member is setovered towards described primary importance; With
One way stop peturn valve, described one way stop peturn valve operationally is being arranged in the described hydraulic circuit in the described second hydraulic pressure bringing device downstream and in the position of described pump upstream and between described secondary volumetric spaces hole and described elementary flow path; When the pressure in the described elementary flow channel that is communicated to described secondary volumetric spaces by described decompression aperture surpasses second threshold pressure value, described boiler check valve allows fluid stream from described secondary volumetric spaces orifice flow to described elementary flow channel, and wherein when described boiler check valve allows fluid flow to cross wherein, the fluid that flow to described secondary volumetric spaces from described elementary flow channel by described decompression aperture has experienced the reduction of pressure, make thus between described secondary volumetric spaces and described elementary flow channel, to have produced difference of pressure, the described valve member of described pressure official post from described primary shaft to location bias to described second axial location; And wherein, when described closure of check ring and when having stopped fluid stream by wherein, described difference of pressure reduces and described biasing member makes described valve member bias to described first axial location, and wherein said first threshold force value is greater than described second threshold pressure value.
9, automobile-used hydraulic efficiency pressure system according to claim 8 is characterized in that, the described first hydraulic pressure bringing device is that hydraulic braking booster device and the described second hydraulic pressure bringing device are the fluid-link steering wheel words.
10, automobile-used hydraulic efficiency pressure system according to claim 8, it is characterized in that, described boiler check valve define for opening described boiler check valve so that fluid flow cross wherein for the resistance of selectively variable, it is adjustable making the described threshold pressure value that is limited by described boiler check valve thus.
11, automobile-used hydraulic efficiency pressure system according to claim 10 is characterized in that, the outside that described boiler check valve is carried out is regulated and optionally changed described resistance.
12, automobile-used hydraulic efficiency pressure system according to claim 8 is characterized in that, described one way stop peturn valve comprises:
Operationally be arranged in the described boiler check valve and second valve member that can between the primary importance and the second place, move, at described primary importance place, described second valve member prevents that fluid flow from crossing described boiler check valve, at described second place place, described second valve member allows fluid flow to cross described boiler check valve;
Make second biasing member of described second valve member towards described primary importance biasing; With
With the threaded member that described biasing member operationally connects, can reorientate from the outside to described threaded member, wherein reorientating of carrying out of described threaded member changed described threshold value.
13, automobile-used hydraulic efficiency pressure system according to claim 8, it is characterized in that described automobile-used hydraulic efficiency pressure system further comprises and operationally is arranged in the described hydraulic circuit and is positioned at the described second hydraulic pressure bringing device downstream and is positioned at the hydraulic pressure storage facility of described pump upstream and wherein said one way stop peturn valve is communicated with described elementary flow channel fluid being positioned at the position that makes described by-pass prot be communicated with residing position upstream with described elementary flow channel fluid.
14, automobile-used hydraulic efficiency pressure system according to claim 8, it is characterized in that, described one way stop peturn valve is set at from described secondary volumetric spaces hole and extends to the fluid line of described elementary flow channel, and described boiler check valve separates by a part and the described pressure relief valve of described fluid line.
15, a kind of automobile-used hydraulic efficiency pressure system, described automobile-used hydraulic efficiency pressure system comprises hydraulic circuit, described hydraulic circuit has by install in series and the Hydraulic Pump that is set up in order along elementary flow path, flow divider valve, the first hydraulic pressure bringing device and the second hydraulic pressure bringing device;
It is characterized in that,
Described hydraulic circuit further comprises and is set at the pressure relief valve between described first hydraulic pressure bringing device and the described second hydraulic pressure bringing device in the described elementary flow path, wherein under first running state, all substantially described hydraulic fluids of discharging from described pump all cycle through described flow divider valve along described elementary flow path and arrive the described first hydraulic pressure bringing device; And when the fluid of the described elementary flow path that is arranged in the described first hydraulic pressure bringing device upstream is increased to first threshold, described flow divider valve will be divided into second fluid stream of first fluid stream that is communicated to the described elementary flow path that is arranged in the described first hydraulic pressure bringing device upstream and the point that is communicated to the described elementary flow path that is positioned at the described first hydraulic pressure bringing device downstream and is positioned at described pressure relief valve upstream by the described hydraulic fluid that described pump is discharged;
Wherein said pressure relief valve has valve body and valve member, described valve body limits valve chamber, described valve chamber limits axis, wherein said valve member can indoorly slide vertically between first axial location and second axial location and described chamber is separated into elementary flow channel and secondary volumetric spaces described, described valve member further limits the decompression aperture, and described decompression aperture provides fluid to be communicated with between described elementary flow channel and described secondary volumetric spaces; Described valve body further limits the ingate that is communicated with described elementary flow channel fluid, the egress hole that is communicated with described elementary flow channel fluid, the secondary volumetric spaces hole that is communicated with described secondary volumetric spaces fluid, and by-pass prot, described by-pass prot is set at axial midway location place, and described secondary volumetric spaces hole is set on the axial sidepiece of described by-pass prot and described ingate is set on the relative axial sidepiece of described by-pass prot with described egress hole, when described valve member is in described first axial positions, described by-pass prot is sealed so that be not communicated with described valve chamber fluid, and when described valve member is in described second axial positions, described by-pass prot is communicated with described elementary flow channel fluid, described pressure relief valve operationally is arranged in the described hydraulic circuit and is positioned at the described first hydraulic pressure bringing device downstream and is positioned at the described second hydraulic pressure bringing device upstream, and wherein said elementary flow path extends to described ingate from the described first hydraulic pressure bringing device, arrive the described second hydraulic pressure bringing device by described elementary flow channel and described egress hole; Described by-pass prot is communicated with described elementary mobile path flow body at the some place that is positioned at the described second hydraulic pressure bringing device downstream and is positioned at described pump upstream;
Biasing member, described biasing member operationally connects with described valve member and described valve member is setovered towards described primary importance; With
One way stop peturn valve, described one way stop peturn valve operationally is being arranged in the described hydraulic circuit in the described second hydraulic pressure bringing device downstream and in the position of described pump upstream and between described secondary volumetric spaces hole and described elementary flow path; When the pressure in the described elementary flow channel that is communicated to described secondary volumetric spaces by described decompression aperture surpasses second threshold pressure value, described boiler check valve allows fluid stream from described secondary volumetric spaces orifice flow to described elementary flow channel, and wherein when described boiler check valve allows fluid flow to cross wherein, the fluid that flow to described secondary volumetric spaces from described elementary flow channel by described decompression aperture has experienced the reduction of pressure, make thus between described secondary volumetric spaces and described elementary flow channel, to have produced difference of pressure, the described valve member of described pressure official post from described primary shaft to location bias to described second axial location; And wherein, when described closure of check ring and when having stopped fluid stream by wherein, described difference of pressure reduces and described biasing member makes described valve member bias to described first axial location, and wherein said boiler check valve define for opening described boiler check valve so that fluid flow cross wherein for the resistance of selectively variable, it is adjustable making described second threshold pressure value thus.
16, automobile-used hydraulic efficiency pressure system according to claim 15 is characterized in that, the described first hydraulic pressure bringing device is that hydraulic braking booster device and the described second hydraulic pressure bringing device are the fluid-link steering wheel words.
17, automobile-used hydraulic efficiency pressure system according to claim 15 is characterized in that, the outside that described boiler check valve is carried out is regulated and optionally changed described resistance.
18, automobile-used hydraulic efficiency pressure system according to claim 15 is characterized in that, described one way stop peturn valve comprises:
Operationally be arranged in the described boiler check valve and second valve member that can between the primary importance and the second place, move, at described primary importance place, described second valve member prevents that fluid flow from crossing described boiler check valve, at described second place place, described second valve member allows fluid flow to cross described boiler check valve;
Make second biasing member of described second valve member towards described primary importance biasing; With
With the threaded member that described biasing member operationally connects, can reorientate from the outside to described threaded member, wherein reorientating of carrying out of described threaded member changed described threshold value.
19, automobile-used hydraulic efficiency pressure system according to claim 15, it is characterized in that described automobile-used hydraulic efficiency pressure system further comprises and operationally is arranged in the described hydraulic circuit and is positioned at the described second hydraulic pressure bringing device downstream and is positioned at the hydraulic pressure storage facility of described pump upstream and described one way stop peturn valve is communicated with described elementary flow channel fluid being positioned at the position that makes described by-pass prot be communicated with residing position upstream with described elementary flow channel fluid.
20, automobile-used hydraulic efficiency pressure system according to claim 15, it is characterized in that, described one way stop peturn valve is set at from described secondary volumetric spaces hole and extends to the fluid line of described elementary flow channel, and described boiler check valve separates by a part and the described pressure relief valve of described fluid line.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US11/901865 | 2007-09-19 | ||
| US11/901,865 US7739943B2 (en) | 2006-09-20 | 2007-09-19 | Vehicular hydraulic system with pressure dump and relief valve arrangement |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201280127Y true CN201280127Y (en) | 2009-07-29 |
Family
ID=40927012
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008200094988U Expired - Fee Related CN201280127Y (en) | 2007-09-19 | 2008-04-29 | Hydraulic system with pressure release and relief valve apparatus for automobile |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201280127Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103802811A (en) * | 2014-01-27 | 2014-05-21 | 李玉喜 | Automatic circulation system and automatic circulation braking system established by same |
| CN113575072A (en) * | 2015-09-28 | 2021-11-02 | 精密种植有限责任公司 | System and apparatus for controlling and monitoring liquid application to agricultural fields |
-
2008
- 2008-04-29 CN CNU2008200094988U patent/CN201280127Y/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103802811A (en) * | 2014-01-27 | 2014-05-21 | 李玉喜 | Automatic circulation system and automatic circulation braking system established by same |
| CN113575072A (en) * | 2015-09-28 | 2021-11-02 | 精密种植有限责任公司 | System and apparatus for controlling and monitoring liquid application to agricultural fields |
| CN113575072B (en) * | 2015-09-28 | 2024-05-17 | 精密种植有限责任公司 | System and apparatus for controlling and monitoring application of farmland liquids |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104358865B (en) | Hydraulic control system with etrs for a continuously variable transmission | |
| US7765915B2 (en) | Vehicular hydraulic system with dual relief valve | |
| CN1862031B (en) | Anti jerk valve | |
| CN107428317A (en) | The brake apparatus with brake circuit/wheel drag of pressure initiation regulation is carried out with the special wiring by inlet valve and for pressure controlled method | |
| WO2006061066A1 (en) | Method for regulating a compressed air supply system of a motor vehicle | |
| DE10209880A1 (en) | System for controlling a hydraulic variable pump | |
| US6877577B1 (en) | Vehicle all-wheel drive system | |
| CN201280127Y (en) | Hydraulic system with pressure release and relief valve apparatus for automobile | |
| CN201280126Y (en) | Hydraulic system with pressure release valve for automobile | |
| US7739943B2 (en) | Vehicular hydraulic system with pressure dump and relief valve arrangement | |
| BG67167B1 (en) | Hydraulic control device | |
| JP2018515730A (en) | Hydraulic drive | |
| CN105972195A (en) | Clutch and torque converter control for a continuously variable transmission | |
| CN201280153Y (en) | Vehicle hydraulic system with pressure release valve | |
| US20080067865A1 (en) | Vehicular hydraulic system with relief valve | |
| CN201220660Y (en) | Vehicle hydraulic system with priority valve and safety valve | |
| CN201231748Y (en) | Vehicle hydraulic system with priority valve | |
| US7779744B2 (en) | Vehicular hydraulic system with priority valve | |
| CN201280128Y (en) | Vehicle hydraulic system | |
| US20070228816A1 (en) | Brake fluid pressure controller for vehicle | |
| CN1186546C (en) | Static water pressure loop pressure regulation valve with reduced input torsion required by static water pressure element | |
| CN106438135A (en) | Relief valve device | |
| US20080066990A1 (en) | Vehicular hydraulic system with pressure reducing valve | |
| US7730825B2 (en) | Vehicular hydraulic system with priority valve and relief valve | |
| US7739942B2 (en) | Vehicular hydraulic system with pressure dump valve |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| ASS | Succession or assignment of patent right |
Owner name: GENERAL MOTORS GLOBAL TECHNOLOGY OPERATING COMPANY Free format text: FORMER OWNER: DELPHI TECHNOLOGY COMPANY Effective date: 20100524 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20100524 Address after: Michigan Patentee after: GM Global Technology Operations, Inc. Address before: Michigan Patentee before: Delphi Technology Inc. |
|
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20090729 Termination date: 20100429 |