CN201280126Y - Hydraulic system with pressure release valve for automobile - Google Patents
Hydraulic system with pressure release valve for automobile Download PDFInfo
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- CN201280126Y CN201280126Y CNU2008200094973U CN200820009497U CN201280126Y CN 201280126 Y CN201280126 Y CN 201280126Y CN U2008200094973 U CNU2008200094973 U CN U2008200094973U CN 200820009497 U CN200820009497 U CN 200820009497U CN 201280126 Y CN201280126 Y CN 201280126Y
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Abstract
A vehicle hydraulic system with a pressure relief valve comprises a pump, a first hydraulic application device and a second hydraulic application device, which are serially arranged, wherein the pressure of the fluid on the upstream of the first hydraulic application device can be increased to a first pressure threshold; and the pressure relief valve is arranged on the downstream of the first hydraulic application device, and the fluid entering the valve flows to the second hydraulic application device through an inlet hole, a primary flow passage and an outlet hole of the valve. The valve comprises a valve component capable of sliding axially in a slim valve chamber to separate the primary flow passage from a low-pressure volume space. The valve also includes a low-pressure hole and a bypass hole for turning the fluid to pass through the second hydraulic application device. The valve component can reach a certain position when applied with a bias pressure, and the fluid can turn to the bypass hole when the pressure in the primary flow passage exceeds a second threshold smaller than the first threshold.
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 efficiency gear.
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 provide a kind of have can be used in the pressure relief valve that comprises in the hydraulic efficiency pressure system that being the first hydraulic pressure bringing device arranged of series connection and the second hydraulic pressure bringing device through the structure simplified, and wherein, the pressure that is arranged in the elementary flow path of the first hydraulic pressure bringing device upstream can be raised and reach first threshold and described pressure relief valve guarantees that the pressure that is positioned at the second hydraulic pressure bringing device place is no more than second threshold value, and wherein said first threshold is greater than described second threshold value.
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, the first hydraulic pressure bringing device and the second hydraulic pressure bringing device.Also be provided with pressure relief valve.Described pressure relief valve has valve body and valve member.Described valve body limits the elongated valve chamber with axis.Described valve member can indoorly slide vertically between first axial location and second axial location and described chamber sealed separation is being become elementary flow channel and low pressure volume space described.Low pressure hole and by-pass prot that described valve body also 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 low pressure volume space fluid.Described by-pass prot is set at axial midway location place, and described low pressure hole is set on the 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, and when described valve member was in described second axial positions, described by-pass prot was communicated with described elementary flow channel fluid.When the rising of the fluid pressure in the described elementary flow channel reaches second threshold value, described valve member moves to described second axial location from described first axial location vertically, and wherein elongated valve chamber, ingate, egress hole, by-pass prot and low pressure hole are the unique fluid communication channels that is limited by pressure relief valve.Described pressure relief valve operationally is arranged in the described hydraulic circuit and is positioned at the downstream of the first hydraulic pressure bringing device and the upstream of the second hydraulic pressure bringing device, wherein said elementary flow path from the first hydraulic pressure bringing device extend to described ingate, egress hole by described elementary flow channel and described valve arrives the second hydraulic pressure bringing device.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 Hydraulic Pump upstream.The hydraulic fluid pressure that just is arranged in the described elementary flow path of the first hydraulic pressure bringing device upstream can raise and reach first threshold, and wherein said first threshold is greater than described second threshold value.
In embodiment more of the present utility model, described automobile-used hydraulic efficiency pressure system also comprises the flow divider valve that operationally is set in place in the downstream of described pump and is arranged in the hydraulic circuit of the described first hydraulic pressure bringing device upstream.When the pressure from the hydraulic fluid that wherein flows through is lower than first threshold, described flow divider valve will be communicated to the point of the described elementary flow path that is arranged in the described first hydraulic pressure bringing device upstream from the fluid of all hydraulic basically that wherein flows through.When the pressure of the hydraulic fluid that flows through described flow divider valve is higher than first threshold, described flow divider valve will be divided into second fluid stream of first fluid stream that is communicated to the described elementary fluid path that is arranged in the described first hydraulic pressure bringing device upstream and the point that is communicated to the described elementary fluid path that is positioned at the described first hydraulic pressure bringing device downstream and is positioned at described pressure relief valve upstream from the flow of hydraulic fluid that wherein flows through.
In other embodiment of the present utility model, 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.
Another kind of form of the present utility model comprises a kind of 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, flow divider valve, the first hydraulic pressure bringing device, pressure relief valve and the second hydraulic pressure bringing device.When the pressure from the hydraulic fluid that wherein flows through is lower than first pressure threshold, described flow divider valve will be communicated to the point of the described elementary flow path that is arranged in the described first hydraulic pressure bringing device upstream from the fluid of all hydraulic basically that wherein flows through.When the pressure of the hydraulic fluid that flows through described flow divider valve is higher than first threshold, described flow divider valve will be divided into second fluid stream of first fluid stream that is communicated to the described elementary fluid path that is arranged in the described first hydraulic pressure bringing device upstream and the point that is communicated to the described elementary fluid path that is positioned at the described first hydraulic pressure bringing device downstream and is positioned at described pressure relief valve upstream from the flow of hydraulic fluid that wherein flows through.When the pressure from the hydraulic fluid that wherein flows through is lower than second pressure threshold, described pressure relief valve will be communicated to the point of the described elementary flow path that is arranged in the described second hydraulic pressure bringing device upstream from the fluid of all hydraulic basically that wherein flows through.When the pressure of the hydraulic fluid that flows through described pressure relief valve is higher than second threshold value, described pressure relief valve will be divided into the 4th fluid stream of the 3rd fluid stream that is communicated to the described elementary fluid path that is arranged in the described second hydraulic pressure bringing device upstream and the point that is communicated to the described elementary fluid path that is positioned at the described second hydraulic pressure bringing device downstream and is positioned at described pump upstream from the flow of hydraulic fluid that wherein flows through.The first threshold that is limited by described flow divider valve is greater than second threshold value that is limited by described pressure relief valve.
Advantage of the present utility model is: provide a kind of permission first hydraulic pressure bringing device and the second hydraulic pressure bringing device to be disposed in series in pressure relief valve in the automobile-used hydraulic circuit, the relieving pressure of the wherein said second hydraulic pressure bringing device is less than the relieving pressure value of the first hydraulic pressure bringing device.
When hydraulic braking that is applied to combine and steering gear ancillary system, allow to use steering gear auxiliary device with pressure releasing value lower than brake auxiliary device.Compare with using the same with the brake auxiliary device at least big steering gear auxiliary device of the hydraulic pressure value of releasing, this will save cost usually.
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 part cross-sectional schematic of the pressure relief valve under the low pressure state; With
Fig. 5 is the part cross-sectional schematic of the valve 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 booster 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 predetermined control pressure status 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 described fluid control pressure Dump valve is 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 (low pressure hole) in the drawings.Hydraulic fluid enters in the valve body 130 by ingate E, state fluid flows in valve chamber 132 and, will be described described running state below by drawing valve body 130 in the one or more holes among hole F, G and the H according to running state in place, described ingate.
Fig. 4 shows the pressure relief valve 120 of working under the low pressure state, wherein the pressure that enters the hydraulic fluid of valve 120 by hole E is lower than second predetermined threshold pressure.When on steering gear auxiliary device 24, not having obvious load, may there be this low-pressure state.Under this state, the stream that enters hole E arrives fluid-link steering gear auxiliary device 24 by the elementary flow channel 135 and the as prescribed route of valve 120 by hole G.
As shown in FIG., valve body 130 can be equipped with connection fittings 136, and described connection fittings extend in the valve chamber 132 and define the hole G of valve 120.Elongated valve chamber 132 has two cylindrical portion sections of coaxially aliging along axis 133, and the first cylindrical portion section 146 has the diameter bigger than the second cylindrical portion section 148.In embodiment as shown in the figure, connection fittings 136 comprise that respective threads engages in the great circle cylindrical portion section 146 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 150, and described hollow tubular partly has the open end 152 that extends in the valve chamber 132.Barrel portion 150 has the littler external diameter of internal diameter than the cylindrical portion section 146 of chamber 132, makes thus to limit clearance space 156 between barrel portion 150 and valve body 130 in valve chamber 132.Barrel portion 150 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 connection fittings 136.Therefore, in the embodiment shown, limit from hole E by the primary fluid passage 135 of valve 120 to hole G by the inner space 137 of clearance space 156, sidewall opening 154 and connection fittings 136.
The back volume space 144 of valve chamber 132 that is positioned at the rear portion of valve member 134 is under the corresponding pressure of pressure with the storage facility 16 that is communicated to back volume space 144 by hole H.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.Valve member 134 sealing separates in low pressure volumetric spaces 144 with the valve chamber 132 and the head seal of valve member 134 between the primary channel 135 that hole G fluid is communicated with and separates and prevent that fluid from flowing between primary channel 135 and low pressure volumetric spaces 144.When the fluid pressure that enters hole E was relatively low, the fluid pressure in the back volume space 144 remained against valve member 134 forward on the connection fittings 136 with the biasing force that is applied by control stray bullet spring 142.In this position, as shown in Figure 4, valve member 134 seal up hole F it is not communicated with valve chamber 132 fluids and the fluid that prevents to enter by hole E by by-pass prot F, one of H leaves.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 referring to Fig. 5, there is shown the state that hole G and primary channel 135 interior pressure surpass the threshold pressure value of valve 120.(when valve member 134 was in as shown in Figure 2 axial positions, the hydraulic fluid in the primary channel 135 was exposed to valve member 134 by the open end 152 of connection fittings 136.) this threshold pressure value determines together by the fluid pressure in the back volume space 144 with by the biasing force that spring 142 applies.Thereby valve 120 is designed the stress level that makes this threshold pressure value the fluid pressure of tap hole G is restricted to the pressure limit value that is not more than steering gear auxiliary device 24.When the pressure in the elementary passage 135 during near this threshold pressure value, be applied to that pressure above the valve 134 cause valve 134 to slide backward to be pressed against on the spring 142 and the back volume space 144 from as shown in Figure 4 first axial location to as shown in Figure 5 second axial location in fluid pressure, in second axial positions as shown in Figure 5, valve 134 separates with the open end 152 of barrel portion 150.In second axial positions as shown in Figure 5, thereby valve 134 has slided backward hole F has been exposed to the main fluid stream that enters valve 120 by hole E.Therefore the mixed flow from the hole C of the outlet of brake auxiliary device 22 and valve 20 that enters hole E will be supplied to hole G and hole F.The result is, in the primary channel 135 and the pressure of the fluid in the hydraulic power lines that extend between hole G and steering gear auxiliary device 24 inlets is released and primary channel 135 in and in the pressure reduction of the fluid at hole E and G place.Therefore, described flow control valve member 134 operations are with the maximum pressure of the hydraulic fluid that flow to steering gear auxiliary device 24 of restriction entrance.
If the pressure after hole F has been exposed out in the primary channel 135 continues to rise, valve member 134 will continue to slide backward in valve chamber 132 so.Thereby make because pressure continues to rise though might design valve chamber 132, hole H and valve member 134, hole H finally will come out, but the structure of as shown in FIG. pressure relief valve does not allow valve member 134 that hole H is exposed in the fluids stream in the primary channel 135.
The use of pressure relief valve 120 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 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 second pressure threshold when making pressure relief valve 120 at the entrance of steering gear auxiliary device 24 relieving pressure by making priority valve 20 residing first pressure threshold 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 steering gear auxiliary device 24, and wherein steering gear auxiliary device 24 has the pressure limit value lower than the pressure limit value of brake auxiliary device 22.Make when occurring causing to arrive no longer state greater than the certain level of the pressure limit value of steering gear auxiliary device 24 that thereby valve 120 designed valve member 134 will and return as shown in Figure 4 position to front slide by the pressure decay that hole E enters the hydraulic fluid of valve 120.
Valve 120 has relatively simply and the pressure relief valve of the structure that is easy to produce for a kind of, and described valve comprises elongated valve chamber 32, ingate E, by-pass prot F, egress hole G and the low pressure hole H as the unique fluid communication channels that is limited by valve 120.In the embodiment shown, elongated valve member 132 comprises two cylindrical portion sections 146,148 with different-diameter as indicated above.Valve member 134 is arranged in the littler part of diameter 148, and the part that described diameter is littler has the elementary flow channel 135 that extends through the bigger part of diameter 146.Part 146 fluids that hole E and G and diameter are bigger are communicated with, and littler part 148 fluids of hole F and H and diameter are communicated with.
Valve 120 also comprises the threaded plunger 140 that connects with biasing member 142 operations.In the embodiment shown, as shown in Figure 4 and Figure 5, biasing member 142 is that an end engages with valve member 134 and the opposite end is positioned at helical spring form on the threaded plunger 140.Thereby plunger 140 has the screw 141 that engages with the matching thread that forms and can regulate the axial location of plunger 140 by plunger 140 is rotated with respect to valve body 130 in valve port 132.Use 140 permissions of this threaded plunger after by the assembling of finishing valve simply with respect to valve body 130 rotary plungers 140, the biasing force that is applied to by spring 142 on the valve member 134 to be carried out the outside adjusting.Under valve member 134 situation that at first the residing control presssure value of exposed hole F is needing to regulate after installing priority valve 120, the threaded plunger 140 feasible obviously easier this adjustings of carrying out.The optional embodiment of other of priority valve 120 also falls in the scope of the present utility model, and in other optional embodiment of priority valve 120, plunger 140 is press-fitted in the valve body 130 and can not carries out that the outside is regulated or valve body 130 is provided with blind hole.
In another optional embodiment of valve 120, expection hole H can be the ambient pressure that exposes, and control presssure will not depend on the pressure in the storage facility 16 thus.In this optional embodiment, the sealing member that is arranged on above the valve member 134 can be used to prevent that hydraulic fluid from producing leakage.Also might use other sealing member that is disposed between environment and the valve member 134, thereby prevent that hydraulic fluid from produce leaking and polluted.
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 steering gear device 24 upstreams 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.
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 efficiency gear and system.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 valve gear 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 valve gear 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 valve gear 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 relief valve as herein described to be used for hydraulic circuit.For example, in the hydraulic circuit that pressure relief valve as herein described 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 relief valve 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 relief valve as herein described 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 might be used for having and be arranged near the storage facility the pump 14 and be arranged near the valve 120 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 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 have by install in series and the Hydraulic Pump that is set up in order along elementary flow path, the first hydraulic pressure bringing device and the second hydraulic pressure bringing device;
It is characterized in that,
Described hydraulic circuit further comprises pressure relief valve, and described pressure relief valve has valve body and valve member; Described valve body limits the elongated valve chamber with axis, and described valve member can indoorly slide vertically between first axial location and second axial location and described chamber sealed separation is become elementary flow channel and low pressure volume space described; Described valve body also 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 low pressure hole and the by-pass prot that are communicated with described low pressure volume space fluid, described by-pass prot is set at axial midway location place, and described low pressure hole is set on the 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, when the rising of the fluid pressure in the described elementary flow channel reaches second threshold value, described valve member moves to described second axial location from described first axial location vertically, and wherein said pressure relief valve operationally is arranged in the described hydraulic circuit and is positioned at the downstream of the first hydraulic pressure bringing device and the upstream of the second hydraulic pressure bringing device, and wherein said elementary flow path extends to described ingate from the first hydraulic pressure bringing device, described egress hole by described elementary flow channel and described valve arrives the described second hydraulic pressure bringing device; 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 Hydraulic Pump upstream; And wherein
The hydraulic fluid pressure that just is arranged in the described elementary flow path of the described first hydraulic pressure bringing device upstream can raise and reach first threshold and described first threshold greater than described second threshold value.
2, automobile-used hydraulic efficiency pressure system according to claim 1, it is characterized in that, described pressure relief valve further comprises the connection fittings that are fixed on a hole that is arranged in described ingate and described egress hole on the described pressure relief valve, described connection fittings limit from the fluid passage of wherein passing through and extend into the described elementary flow channel, when described valve member is in described first axial positions, described valve member engages with described connection fittings, and when described valve member is in described second axial positions, described valve member and described connection fittings axially-spaced.
3, automobile-used hydraulic efficiency pressure system according to claim 1 is characterized in that, described automobile-used hydraulic efficiency pressure system further comprises:
Biasing member, described biasing member be set in the described low pressure volume space of described pressure relief valve and towards described primary shaft to the described valve member of position axial bias; With
Threaded member, described threaded member connects with the operation of described biasing member, can axially reorientate from the outside to described threaded member, wherein axially reorientating of carrying out of described threaded member has been regulated described second threshold value.
4, 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 hydraulic pressure storage facility that is set at described second hydraulic pressure bringing device downstream and described pump upstream, and described low pressure hole is communicated with described hydraulic pressure storage facility fluid.
5, automobile-used hydraulic efficiency pressure system according to claim 1, it is characterized in that, described valve chamber comprises cylindrical substantially first section and cylindrical substantially second section, and wherein said first cylindrical portion section and the described second cylindrical portion section coaxially are provided with and the described first cylindrical portion section has diameter than the described second cylindrical portion Duan Gengda; Described ingate and described egress hole are communicated with the described first cylindrical portion section fluid, and described low pressure hole and described by-pass prot are communicated with the described second cylindrical portion section fluid;
Connection fittings are set in first hole in described ingate and the described egress hole, described connection fittings limit from the fluid passage of wherein passing through and comprise the hollow tubular part, described hollow tubular partly has the open end that extends in the described first cylindrical portion section, at least one sidewall opening in the described barrel portion provides fluid to be communicated with between described fluid passage and the clearance space that is limited between described barrel portion and the described first cylindrical portion section, second hole in described ingate and the described egress hole is communicated with described clearance space fluid, when described valve member is in described first axial positions, described valve member and the described open end of described barrel portion engage and are exposed in the fluid in the described fluid passage, when described valve member is in described second axial positions, the described open end axially-spaced of described valve member and described barrel portion.
6, automobile-used hydraulic efficiency pressure system according to claim 5 is characterized in that, described automobile-used hydraulic efficiency pressure system further comprises:
Biasing member, described biasing member are set in the described second cylindrical portion section and the described valve member of bias voltage makes it engage with described connection fittings formation; With
Threaded member, described threaded member engages with described valve body at an end place of the contiguous described second cylindrical portion section and connects with described biasing member operation, can axially reorientate from the outside to described threaded member, wherein axially reorientating of carrying out of described threaded member regulated described second threshold value.
7, automobile-used hydraulic efficiency pressure system according to claim 1 is characterized in that, the described first hydraulic pressure bringing device is the hydraulic braking booster device.
8, automobile-used hydraulic efficiency pressure system according to claim 1 is characterized in that, the described second hydraulic pressure bringing device is the fluid-link steering wheel word.
9, 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 flow divider valve that operationally is set in place in the downstream of described pump and is arranged in the described hydraulic circuit of the described first hydraulic pressure bringing device upstream, when the pressure from the hydraulic fluid that wherein flows through is lower than described first threshold, described flow divider valve will be communicated to the point of the described elementary flow path that is arranged in the described first hydraulic pressure bringing device upstream from the fluid of all hydraulic basically that wherein flows through; When the pressure of the hydraulic fluid that flows through described flow divider valve is higher than described first threshold, described flow divider valve will be divided into second fluid stream of first fluid stream that is communicated to the described elementary fluid path that is arranged in the described first hydraulic pressure bringing device upstream and the point that is communicated to the described elementary fluid path that is positioned at the described first hydraulic pressure bringing device downstream and is positioned at described pressure relief valve upstream from the flow of hydraulic fluid that wherein flows through.
10, a kind of automobile-used hydraulic efficiency pressure system, described automobile-used hydraulic efficiency pressure system comprises:
Hydraulic circuit, described hydraulic circuit have 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 when the pressure from the hydraulic fluid that wherein flows through is lower than first pressure threshold, described flow divider valve will be communicated to the point of the described elementary flow path that is arranged in the described first hydraulic pressure bringing device upstream from the fluid of all hydraulic basically that wherein flows through; When the pressure of the hydraulic fluid that flows through described flow divider valve is higher than described first threshold, described flow divider valve will be divided into second fluid stream of first fluid stream that is communicated to the described elementary fluid path that is arranged in the described first hydraulic pressure bringing device upstream and the point that is communicated to the described elementary fluid path that is positioned at the described first hydraulic pressure bringing device downstream and is positioned at described pressure relief valve upstream from the flow of hydraulic fluid that wherein flows through;
Wherein when the pressure from the hydraulic fluid that wherein flows through is lower than second pressure threshold, described pressure relief valve will be communicated to the point of the described elementary flow path that is arranged in the described second hydraulic pressure bringing device upstream from the fluid of all hydraulic basically that wherein flows through; When the pressure of the hydraulic fluid that flows through described pressure relief valve is higher than second threshold value, described pressure relief valve will be divided into the 4th fluid stream of the 3rd fluid stream that is communicated to the described elementary fluid path that is arranged in the described second hydraulic pressure bringing device upstream and the point that is communicated to the described elementary fluid path that is positioned at the described second hydraulic pressure bringing device downstream and is positioned at described pump upstream from the flow of hydraulic fluid that wherein flows through; And
Wherein said first threshold is greater than described second threshold value.
11, automobile-used hydraulic efficiency pressure system according to claim 10 is characterized in that, the described first hydraulic pressure bringing device is the hydraulic braking booster device.
12, automobile-used hydraulic efficiency pressure system according to claim 10 is characterized in that, the described second hydraulic pressure bringing device is the fluid-link steering wheel word.
13, automobile-used hydraulic efficiency pressure system according to claim 10 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.
14, a kind of automobile-used hydraulic efficiency pressure system, described automobile-used hydraulic efficiency pressure system comprises:
Hydraulic circuit, described hydraulic circuit have by install in series and the Hydraulic Pump that is set up in order along elementary flow path, hydraulic braking booster device and fluid-link steering wheel word;
It is characterized in that,
Described hydraulic circuit further comprises pressure relief valve, and described pressure relief valve has valve body and valve member; Described valve body limits the elongated valve chamber with axis, and described valve member can indoorly slide vertically between first axial location and second axial location and described chamber sealed separation is become elementary flow channel and low pressure volume space described; Described valve body also 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 low pressure hole and the by-pass prot that are communicated with described low pressure volume space fluid, described by-pass prot is set at axial midway location place, and described low pressure hole is set on the 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, when the rising of the fluid pressure in the described elementary flow channel reaches certain threshold value, described valve member moves to described second axial location from described first axial location vertically, and wherein said elongated valve chamber, described ingate, described egress hole, described by-pass prot and described low pressure hole are the unique fluid communication channels that is limited by described pressure relief valve; And wherein said pressure relief valve operationally is arranged in the described hydraulic circuit and is positioned at the downstream of described hydraulic braking booster device and the upstream of described fluid-link steering wheel word, wherein said elementary flow path from described hydraulic braking booster device extend to described ingate, described egress hole by described elementary flow channel and described valve arrives described fluid-link steering wheel word; Described by-pass prot is communicated with described elementary mobile path flow body at the some place that is positioned at described fluid-link steering wheel word downstream and is positioned at described Hydraulic Pump upstream; And wherein
The hydraulic fluid pressure that just is arranged in the described elementary flow path of described hydraulic braking booster device upstream can raise and reach first threshold and described first threshold greater than described second threshold value.
15, automobile-used hydraulic efficiency pressure system according to claim 14, it is characterized in that, described automobile-used hydraulic efficiency pressure system further comprises the flow divider valve that operationally is set in place in the downstream of described pump and is arranged in the described hydraulic circuit of described hydraulic braking booster device upstream, when the pressure from the hydraulic fluid that wherein flows through is lower than described first threshold, described flow divider valve will be communicated to the point of the described elementary flow path that is arranged in described hydraulic braking booster device upstream from the fluid of all hydraulic basically that wherein flows through; When the pressure of the hydraulic fluid that flows through described flow divider valve is higher than described first threshold, described flow divider valve will be divided into second fluid stream of first fluid stream that is communicated to the described elementary fluid path that is arranged in described hydraulic braking booster device upstream and the point that is communicated to the described elementary fluid path that is positioned at described hydraulic braking booster device downstream and is positioned at described pressure relief valve upstream from the flow of hydraulic fluid that wherein flows through.
16, automobile-used hydraulic efficiency pressure system according to claim 15, it is characterized in that, described pressure relief valve further comprises the connection fittings that are fixed on a hole that is arranged in described ingate and described egress hole on the described pressure relief valve, described connection fittings limit from the fluid passage of wherein passing through and extend into the described elementary flow channel, when described valve member is in described first axial positions, described valve member engages with described connection fittings, and when described valve member is in described second axial positions, described valve member and described connection fittings axially-spaced.
17, automobile-used hydraulic efficiency pressure system according to claim 15 is characterized in that, described automobile-used hydraulic efficiency pressure system further comprises:
Biasing member, described biasing member be set in the described low pressure volume space of described pressure relief valve and towards described primary shaft to the described valve member of position axial bias; With
Threaded member, described threaded member connects with the operation of described biasing member, can axially reorientate from the outside to described threaded member, wherein axially reorientating of carrying out of described threaded member has been regulated described second threshold value.
18, automobile-used hydraulic efficiency pressure system according to claim 15, it is characterized in that, described automobile-used hydraulic efficiency pressure system further comprises the hydraulic pressure storage facility that is set at described fluid-link steering wheel word downstream and described pump upstream, and described low pressure hole is communicated with described hydraulic pressure storage facility fluid.
19, automobile-used hydraulic efficiency pressure system according to claim 15, it is characterized in that, described valve chamber comprises cylindrical substantially first section and cylindrical substantially second section, and wherein said first cylindrical portion section and the described second cylindrical portion section coaxially are provided with and the described first cylindrical portion section has diameter than the described second cylindrical portion Duan Gengda; Described ingate and described egress hole are communicated with the described first cylindrical portion section fluid, and described low pressure hole and described by-pass prot are communicated with the described second cylindrical portion section fluid;
Connection fittings are set in first hole in described ingate and the described egress hole, described connection fittings limit from the fluid passage of wherein passing through and comprise the hollow tubular part, described hollow tubular partly has the open end that extends in the described first cylindrical portion section, at least one sidewall opening in the described barrel portion provides fluid to be communicated with between described fluid passage and the clearance space that is limited between described barrel portion and the described first cylindrical portion section, second hole in described ingate and the described egress hole is communicated with described clearance space fluid, when described valve member is in described first axial positions, described valve member and the described open end of described barrel portion engage and are exposed in the fluid in the described fluid passage, when described valve member is in described second axial positions, the described open end axially-spaced of described valve member and described barrel portion.
20, automobile-used hydraulic efficiency pressure system according to claim 19 is characterized in that, described automobile-used hydraulic efficiency pressure system further comprises:
Biasing member, described biasing member are set in the described second cylindrical portion section and the described valve member of bias voltage makes it engage with described connection fittings formation; With
Threaded member, described threaded member engages with described valve body at an end place of the contiguous described second cylindrical portion section and connects with described biasing member operation, can axially reorientate from the outside to described threaded member, wherein axially reorientating of carrying out of described threaded member regulated described second threshold value.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US11/901,863 US7739942B2 (en) | 2006-09-20 | 2007-09-19 | Vehicular hydraulic system with pressure dump valve |
| US11/901863 | 2007-09-19 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201280126Y true CN201280126Y (en) | 2009-07-29 |
Family
ID=40927011
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008200094973U Expired - Fee Related CN201280126Y (en) | 2007-09-19 | 2008-04-29 | Hydraulic system with pressure release valve for automobile |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201280126Y (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103032413A (en) * | 2012-12-27 | 2013-04-10 | 中国航空工业集团公司金城南京机电液压工程研究中心 | Safe and stable valve for hydraulic servo system |
| CN103625457A (en) * | 2012-08-28 | 2014-03-12 | 北汽福田汽车股份有限公司 | One-way pressure regulating valve |
| CN114144612A (en) * | 2019-06-11 | 2022-03-04 | 卡派勒未来有限责任公司 | Release valve |
-
2008
- 2008-04-29 CN CNU2008200094973U patent/CN201280126Y/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103625457A (en) * | 2012-08-28 | 2014-03-12 | 北汽福田汽车股份有限公司 | One-way pressure regulating valve |
| CN103625457B (en) * | 2012-08-28 | 2016-01-13 | 北汽福田汽车股份有限公司 | One-way pressure regulating valve |
| CN103032413A (en) * | 2012-12-27 | 2013-04-10 | 中国航空工业集团公司金城南京机电液压工程研究中心 | Safe and stable valve for hydraulic servo system |
| CN103032413B (en) * | 2012-12-27 | 2015-09-16 | 中国航空工业集团公司金城南京机电液压工程研究中心 | A kind of for Hydrauservo System safety and stability valve |
| CN114144612A (en) * | 2019-06-11 | 2022-03-04 | 卡派勒未来有限责任公司 | Release valve |
| CN114144612B (en) * | 2019-06-11 | 2023-11-24 | 卡派勒未来有限责任公司 | Relief valve |
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Owner name: GENERAL MOTORS GLOBAL TECHNOLOGY OPERATING COMPANY Free format text: FORMER OWNER: DELPHI TECHNOLOGY COMPANY Effective date: 20100524 |
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| C41 | Transfer of patent application or patent right or utility model | ||
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