CN102616105A - Valve unit - Google Patents

Valve unit Download PDF

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Publication number
CN102616105A
CN102616105A CN2011103919353A CN201110391935A CN102616105A CN 102616105 A CN102616105 A CN 102616105A CN 2011103919353 A CN2011103919353 A CN 2011103919353A CN 201110391935 A CN201110391935 A CN 201110391935A CN 102616105 A CN102616105 A CN 102616105A
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CN
China
Prior art keywords
valve
control
lifting
load
suspension
Prior art date
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Granted
Application number
CN2011103919353A
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Chinese (zh)
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CN102616105B (en
Inventor
S·黑尔
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Haldex Brake Products AB
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Haldex Brake Products GmbH
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Filing date
Publication date
Application filed by Haldex Brake Products GmbH filed Critical Haldex Brake Products GmbH
Publication of CN102616105A publication Critical patent/CN102616105A/en
Application granted granted Critical
Publication of CN102616105B publication Critical patent/CN102616105B/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
    • B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
    • B60G17/052—Pneumatic spring characteristics
    • B60G17/0523—Regulating distributors or valves for pneumatic springs
    • B60G17/0525—Height adjusting or levelling valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
    • B60G17/0152—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit
    • B60G17/0155—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit pneumatic unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
    • B60G17/018—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the use of a specific signal treatment or control method
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
    • B60G17/019—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the type of sensor or the arrangement thereof
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
    • B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
    • B60G17/052—Pneumatic spring characteristics
    • B60G17/0521—Pneumatic spring characteristics the spring having a flexible wall
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
    • B60G2400/60—Load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
    • F16F9/04—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum in a chamber with a flexible wall

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

The invention relates to a valve unit (6) for a vehicle having a shaft suspended at a metal suspension spring. The vale unit (6) comprises a housing (11), which has a supply port (7) for connection to a supply pipeline of a pressurized air source, a lifting corrugated pipe port (9) for lifting a lifting corrugated pipe (4) of the shaft (3), and a suspension corrugated pipe port (10) for lifting a suspension corrugated pipe (5) of the shaft (3). The housing comprises a lifting corrugated pipe vale (13) for controlling the pressure of the lifting corrugated pipe port (9). In addition, the housing comprises a suspension corrugated pipe valve (14) for controlling the pressure of the suspension corrugated pipe port (10). Furthermore, the housing comprises at least one load depending control valve (12) for pneumatically controlling the lifting corrugated pipe vale (13) and/or the suspension corrugated pipe valve (14).

Description

Valve cell
Technical field
The present invention relates to be used for the valve cell of vehicle, particularly tractor truck or trailer, said vehicle has the axle that is suspended at steel axle spring place.And, the invention still further relates to this valve cell have by the metal suspension spring suspension the axle vehicle in application.
Background technology
Although be equipped with the commercial vehicle of the airsuspension system that is used for a plurality of or the quantity of all-service vehicle to increase; But still has the all-service vehicle that is equipped with the metal suspension spring; This is because compare with airsuspension system, and the cost of these metal suspension systems reduces, sturdy and durable and be easier to safeguard.And, be well known that, be equipped with additional lifting axis for vehicle with the axle that is suspended at metal suspension spring place.Lifting axis is lower than in the load of vehicle under the situation of threshold value load and is not used.Yet, surpassing under the situation of threshold value load in the load of vehicle, lifting axis is caught to contact with the road surface, to be used to providing the additional of vehicle to suspend.Lifting axis generally includes lifting bellows and at least one suspension bellow.At the dead status of the lifting axis that is lower than threshold value load, the lifting bellows is pressurized, make axle than the chassis near vehicle, and suspension bellow is deflated.On the contrary, in the initiate mode of lifting axis, the lifting bellows is deflated, and suspension bellow is inflated.
In the prior art systems relevant with the vehicle that comprises metal suspension spring and pneumatically actuated lifting axis; Pneumatically actuatedly carry out through pneumatic circuit; Said pneumatic circuit is configured reservoir, pressure regulator, load-sensing valve and the control cock of forced air, and said control cock is controlled in the lifting bellows and the Pneumatic pressure in the suspension bellow.Above-mentioned pneumatic members connects through pneumatic line.Load-sensing valve (its be supported on chassis place) is connected the indicating device that car load is provided with additional mechanical between spool (it contacts by the metal suspension spring suspension and with the road surface all the time).
Summary of the invention
The objective of the invention is, a kind of improved pneumatic members that is used for the pneumatic circuit of lifting axis is provided, said pneumatic circuit is used for having the vehicle by the axle of metal suspension spring suspension.
A solution of above-mentioned purpose of the present invention is provided by a kind of valve cell according to independent claims 1.Other embodiment of this solution are limited dependent claims 2-22.Another solution of above-mentioned purpose of the present invention is provided by independent claims 23.
The present invention proposes to use a kind of valve cell of compactness, and the valve cell of said compactness can be to be designed to and to be applicable to the vehicle of particular type or a kind of specific valve cell of axle construction.And can make valve cell is modular valve cell, and wherein, a kind of combination of a plurality of submodules is used for a kind of vehicle or axle construction, and the combination of the another kind of submodule is used for another kind of vehicle or axle construction.
Valve cell of the present invention comprises housing (housing by a global facility or a plurality of parts or a plurality of modules constitutes).Casing structure goes out to be used to be connected to the supply port of the feed pipe of pressurized air source, for example reservoir.And housing also comprises the lifting bellows bonded assembly lifting corrugated tube port that is used for valve cell and lifting axis.Housing also constructs the suspension bellow port, and said suspension bellow port is used for valve cell is connected with (at least one) suspension bellow of lifting axis.In the simple embodiment of valve cell of the present invention, the corresponding pipeline of with three ports, promptly supplying with port, lifting corrugated tube port and suspension bellow port and valve cell couples together and just is enough to valve cell is integrated in the pneumatic circuit.Therefore, the work capacity that is used for valve cell of the present invention is integrated into pneumatic circuit is reduced.(in addition, other machineries, electricity and/or pneumatic connection can be provided also.)
According to the present invention, housing is not only to comprise a valve but a plurality of valve:
-at least one lifting bellows valve is integrated in the housing.The lifting axis bellows valve is used to control the pressure at lifting corrugated tube port place.This is connected with the lifting corrugated tube port lifting corrugated tube port inflation is carried out through supplying with port at a switching state via the lifting bellows valve usually.On the contrary, at the switching state of the venting of lifting bellows valve, by means of the lifting bellows valve, lifting corrugated tube port and atmosphere, thus allow forced air to flow to atmosphere from the lifting corrugated tube port.
-and at least one suspension bellow valve is integrated in the housing.The suspension bellow valve is used to control the pressure of suspension bellow port.This makes the suspension bellow port and supplies with port and be connected and carry out through the inflation switching state at the suspension bellow valve usually.At the switching state of the venting of suspension bellow valve, suspension bellow port and atmosphere flow to atmosphere to allow forced air from the suspension bellow port.
-in addition, at least one load dependence control cock is integrated in the housing.Load dependence control cock is pneumatically controlled the switching state of lifting bellows valve and/or suspension bellow valve.According to the load of vehicle or the axle of vehicle, load dependence control cock produces and is used for lifting bellows valve and/or suspension bellow valve are switched to the deflated state pneumatic control signal of (or on the contrary) from inflated condition.
Can and be arranged in load dependence control cock and the relevant pneumatic line of housing at lifting bellows valve, the suspension bellow valve of the terminal assembled valve unit of manufacturing line, distribute a plurality of modules of integral type valve cell or valve cell then.When being integrated into valve cell in the vehicle, need not connect control step with integrated lifting bellows valve, suspension bellow valve and load dependence control cock.As long as will supply with the outer associated pipe of port, lifting corrugated tube port and suspension bellow port and valve cell couples together just enough.Pneumatic connection in addition also can additionally make up.Can make also that mechanical connection is assembled to be used for load dependence control cock and/or to make to be electrically connected to be established for valve cell and electric control unit, power supply, signal wire (SW) are coupled together; Said signal wire (SW) has and the load of vehicle or the relevant signal of level height of axle, in electric control unit and similar units, to confirm the load of vehicle.
In a word, valve cell of the present invention has the compact design that reduces manufacturing cost and assembly cost.And valve cell and housing thereof form a kind of compactness and failure-free unit, wherein, pipeline be connected since housing be prevented from being damaged.
According to another embodiment of the invention, valve cell comprises reservoir.This reservoir can be integrated in the housing.According to another embodiment, housing can comprise the port that is used to be connected to reservoir, and said reservoir is positioned at outside the housing.In addition; Do not having under the situation of this reservoir, the dynamic property characteristic of the pilot piping between load dependence control cock and lifting bellows valve and/or the suspension bellow valve can be designed any desired pneumatic power through the pipeline cross-sectional plane of pneumatic members, throttle structure and similarity piece and learn performance.Yet, according to the present invention reservoir is integrated into and particularly produces following advantage in load dependence control cock or the pilot piping:
-reservoir constructs a kind of throttle structure or filter, is used for smoothly falling the high frequency dynamic property characteristic of the control presssure that provides through load dependence control cock.For example, through under the situation of uneven road surface, the control signal of filtered can make lifting bellows valve and/or suspension bellow valve produce bad change action at once at vehicle.The integrated of reservoir will smoothly fall these effects, and the kinetics function that only has longer attenuation process just has control action to load dependence control cock.Usually, this effect also can only be produced by flow regulating valve.Yet, possibly need the opening cross-section of flow regulating valve to have very little cross-sectional plane.This causes following deficiency: the little particle that is included in the forced air can cause the opening cross-section of flow regulating valve to be stopped up.
-on the other hand, reservoir forms the pressurized air source that can be used for controlling lifting bellows valve and/or suspension bellow valve.Be not provided with under the situation that reservoir and pilot piping only have little volume, the increase of control presssure can cause valve change action startup and the pressure in the pilot piping is acutely descended.This pressure decay can produce following danger: valve is switched once more turns back to disadvantageous reference position.This result can avoid through reservoir provided by the invention.
The volume of reservoir can be selected according to the dynamics of the expectation of the control surface of the control surface of lifting bellows valve, suspension bellow valve and control presssure based on the variation of load and/or the uneven situation of ground-surface.
Design for load dependence control cock has multiple choices.Load dependence control cock can be that a single valve maybe can make up through the valve of a plurality of relevant separation.According to one embodiment of present invention, load dependence control cock comprises mechanically actuated control cock, particularly the load-sensing valve.Mechanically actuated load-sensing valve is known from the level height valve usually.These valves form and a kind ofly are used to make up the simple of load dependence control cock but reliable solution.For this design, the valve cell with mechanically actuated control cock can be positioned at the axle place, and wherein, the distance between the chassis of vehicle and the axle is given load dependence control cock by mechanical feedback.This can accomplish through bar.For another embodiment, this realizes that through throw of lever wherein, an end regions of throw of lever is connected with axle, and another end regions of throw of lever is connected with the mechanically actuated control cock that is kept by the chassis.Yet, also can make mechanically actuated control cock be positioned at the chassis place of vehicle, and throw of lever " stride across " mechanically actuated control cock with by the metal suspension supported by springs relevant spool between distance.
According to an optional embodiment of the present invention, load dependence control cock comprises by the electromagnetic valve of electronic control unit basis from the electric signal control of the sensor of senses vehicle load.At this, electronic control unit can be the part of valve cell, for example is integrated in the housing or as independent module to be installed on the housing of valve cell with " flange " mode.Yet, also can make electronic control unit be positioned at the outside of valve cell, and communicate by letter with valve cell through suitable port.In load dependence control cock, use electromagnetic valve that the possibility of various control policies is provided.And, also can in electronic control unit, consider the multiple operating parameter of vehicle, to confirm to be used for the control signal of electromagnetic valve.Also can make electronic control unit that trouble diagnosing is provided, for example in the pipeline of valve cell or under the situation of the outside of valve cell generation leakage and/or under the situation of vehicle overload.Yet, also can make electronic control unit that a kind of mouth of communicating by letter with other electronic control units is provided, for example by means of the CAN bus.
Design for load dependence control cock has multiple choices.According to one embodiment of present invention, load dependence control cock is constructed with the load-sensing valve with by second control cock of load-sensing valve air operated control.At this, the load-sensing valve can be the electric operated valve that switches through electric signal according to load.Yet also can make the load-sensing valve is mechanical load sensing valve.Embodiment according to the present invention, the function of load dependence control cock is divided into two kinds of functions, accomplishes a kind of function by the load-sensing valve and second control cock respectively.The load-sensing valve is used for the load of detection vehicle and produces control signal according to the load that detects.On the contrary, second control cock is used for based on the output switching of being supplied with by the load-sensing valve and is used for producing control signal at the output of second control cock.The control signal of the output of second control cock is also relevant with the load that the load-sensing valve detects.The control signal of the output of second control cock is used to control lifting bellows valve and/or suspension bellow valve.
The mouth that can make the load-sensing valve only with second control cock control or control port is connected, wherein, the input end of second control cock uses the forced air of from another source, for example supplying with port.According to another embodiment of the invention, the mouth of load-sensing valve all is connected with the control port of second control cock and the input end of second control cock.This embodiment uses second control cock to control advantageous particularly under the situation of lifting bellows valve and/or suspension bellow valve in the design of relay valve.Be switched in second control cock under the situation of open mode, second control cock provides the delivery pressure signal that is used by relay valve, to produce and the ratio that is output into of second control cock or relevant output.
Usually, the delivery pressure of load-sensing valve is also relevant with other parameters beyond the car load.One of such parameter is the pressure at input port place.Under the situation that the influence of interested this parameter reduces, one embodiment of the present of invention suggestion input port is connected with load dependence control cock via the pressure confinement valve.This pressure confinement valve is used for the input pressure of load dependence control cock is remained in the preset range, and said preset range is given by the characteristic of pressure confinement valve.
In one embodiment of the invention, second control cock as the part of load dependence control cock is the 3/2-valve.This 3/2-valve is a kind of valve that simply has the cost reliability and durability characteristic and low.
Design for lifting bellows valve and/or suspension bellow valve has multiple choices.The present invention also advises lifting bellows valve and/or suspension bellow valve are designed to the 3/2-valve, and this also can simplify the design of valve cell and make it have reliable characteristic and low cost.
According to another embodiment of the invention, lifting bellows valve and/or suspension bellow valve are relay valves.These relay valves are used for producing according to the control presssure of relay valve the variation of air-flow or condition.A significant advantage of this relay valve is that big flow cross section can be provided at the relay valve place.Aspect the quick change of the volume of the forced air in lifting bellows and/or suspension bellow, this is particularly advantageous.The use of relay valve is guaranteed, can inflate and venting these bellowss with big volume pneumatic flowrate.
Cross-sectional plane for the valve of valve cell can use any design.According to one embodiment of present invention, load dependence control cock, second control cock, lifting bellows valve and/or suspension bellow valve have be used for forced air with have the hole or the cooresponding flow cross section of pipeline of 9mm diameter at least.These minimum cross-sectional planes are guaranteed big flowing velocity and rate of volume flow, so that bellows is inflated apace and exitted.
Usually, the same mouth of second control cock can be used for controlling lifting bellows valve and suspension bellow valve.Yet according to another embodiment of the invention, second control cock has two mouths.First mouth is used to control the lifting bellows valve, and another mouth is used to control the suspension bellow valve.In embodiment of design-calculated of the present invention, second control cock is the 5/2-valve.Usually, launching of lifting axis needs the venting of lifting bellows, and the suspension bellow inflation.Under the situation of single mouth control lifting bellows valve that uses second control cock and suspension bellow valve, single mouth designs relative another valve of a valve in lifting bellows valve and the suspension bellow valve needs reversedly.Need not put upside down under the situation of valve ground using these valves, required control presssure can provide through using second control cock, the form that it has two mouths and has the pressure of putting upside down at these mouths.
Second control cock can have the fixing switch pressure of the type that adapts to the vehicle that has used valve cell.Yet second control cock also can have adjustable switch pressure.The adjusting of switch pressure can be used for making valve cell to adapt to manufacturing errors.Yet, in the loop that the adjusting of the switch pressure of second control cock also can be used for making valve cell be applicable to different vehicle.
For another embodiment of the present invention, the load-sensing valve is connected with second control cock via throttle structure.This throttle structure can have fixed characteristic.According to another embodiment, this throttle structure is adjustable.Throttle structure can be used for smoothly falling the big dynamic oscillation of the load dependence control signal that possibly caused by Uneven road.The adjusting of throttle structure can be used for making valve cell to be applicable to different loops or vehicle.
Usually, lifting bellows valve and/or suspension bellow valve comprise the port that is communicated to atmosphere, so that the venting of connected bellows.According to one embodiment of present invention, lifting bellows valve and/or suspension bellow valve are communicated with deflation hole via the residual pressure valve.This residual pressure valve is guaranteed, in bellows, maintains the minimum pressure that is enough to avoid damaging bellows.
For lifting bellows valve and/or suspension bellow valve, can use any design.According to one embodiment of present invention, lifting bellows valve and/or suspension bellow valve are made up by the combination of 2/2-valve and 3/2-valve.2/2-valve and 3/2-valve are respectively through corresponding load dependence control cock control.This load dependence control cock that is used to control 2/2-valve and 3/2-valve is that load according to vehicle is by the electronically controlled electromagnetic valve of electronic control unit.At this, the 3/2-valve comprises first switching state of the venting of being responsible for relevant bellows and second switching state relevant with the inflation of relevant bellows.Yet, be used to make the input end of bellows inflation or venting to block through the closure state of 2/2-valve.The respective combination that the suspension bellow valve is controlled in the combination and being used to that is used to control 2/2-valve and the 3/2-valve of lifting bellows valve can be controlled by an electronic control unit individually or jointly.
Usually, lifting bellows valve and suspension bellow valve can pass through independent valve constitution.Yet a kind of very compact design can be constructed through lifting bellows valve and suspension bellow valve being integrated in single valve gear, particularly the 5/2-valve controlled by at least one load dependence control cock or the 6/3-valve.This all-in-one-piece 5/2-valve or 6/3-valve guarantee to have identical switching state for the lifting bellows valve with the suspension bellow valve.
According to another embodiment of the invention, lifting bellows valve and/or suspension bellow valve are through electric control signal and through the pneumatic control signal operation.At common motoring condition, control provides through pneumatic control signal.Redundant Control through electric control signal is used to increase the selection that is used to control lifting bellows valve and/or suspension bellow valve.This can be used for the lifting lifting axis under the situation that detects the vehicle backward.Also can be based on electric control signal lifting lifting axis under the situation that vehicle stops.And, can use electric control signal to increase the tractive force of vehicle at non-safety traffic state: detecting or predicting under the situation of this motoring condition, but the lifting lifting axis to increase the load at other places that are braked.
And the lifting bellows valve can be through the delivery pressure control of suspension bellow valve.This is a kind of selection that is used to guarantee the relevant switching state of lifting bellows valve and suspension bellow valve.
According to another embodiment of the invention, the suspension bellow valve is the 4/3-valve with two mouths.These mouths are connected with two suspension bellows, and said two suspension bellows are associated with the not homonymy of vehicle.In the 4/3-valve, to two of vehicle the mouth of homonymy can connect through throttle structure.When vehicle when detour goes, throttle structure advantageous particularly-at this, throttle structure avoided forced air with suspension bellow that the not homonymy of vehicle is associated between quick exchange, and this can cause the instability of going.
According to another embodiment of the present invention, housing comprises and is used to receive moving ahead or the electric port of the signal of backward of expression vehicle.For a unusual simple embodiment of the present invention, sort signal can be the signal relevant with the electric signal of the backing-up lamp of vehicle or such signal.This electric signal can be used for the lifting lifting axis in valve cell in the backward process.
For an alternative embodiment of the invention; Valve cell comprises electronic control unit and/or pilot piping; When detecting or predicting the backward direction, said electronic control unit and/or pilot piping (directly or indirectly) control load dependence control cock, suspension bellow valve and/or lifting bellows valve and make the state be in lifting axis with lifting.Need it from using under the situation of lifting axis among the embodiment of alignment or controllable function at hind axle, this is particularly advantageous, and vehicle and lifting axis move along direction forward.Through lifting lifting axis under the situation of backward, avoided the unstable or damage of lifting axis.
For another solution of the object of the invention, the present invention proposes above-mentioned valve cell is used for vehicle, particularly tractor truck, and said vehicle has the axle by the metal suspension spring suspension.
Use at least a portion valve of electronic control unit controls valve cell to have the following advantages: the control policy that can receive to use in the electronic control unit at the distribution of load by the axle place of metal suspension spring suspension and lifting axis place influences.According to first strategy; Suspension bellow is made in optimum regime by the air pressurized of this amount, has been loaded their maximum load by metal suspension supported by springs axle; And the load at lifting axis place drops to minimum possible value, with the maxim of the load that is no more than other places.For another possible strategy, suspension bellow is pressurized, and purpose is that load is evenly distributed on all axles as far as possible.
After referring to following accompanying drawing and detailed description, other features and advantages of the present invention will become obvious for those skilled in the art.In the scope of the present invention that claims limit, can comprise all these supplementary features and advantage at this.
Description of drawings
Can understand the present invention better referring to accompanying drawing.Each member in the accompanying drawing is not necessary proportional drafting, on the contrary, focuses on clearly explaining principle of the present invention.In institute's drawings attached, identical Reference numeral is represented corresponding parts.
Fig. 1 is the scheme drawing that is integrated in the valve cell of the present invention in the loop, and said loop has pressurized air source and the lifting bellows and at least one suspension bellow relevant with lifting axis.
Fig. 2-the 18th is integrated in the schematic functional diagram of the valve cell of the present invention in the pneumatic circuit relevant with lifting axis.
Figure 19 is the more detailed view of an embodiment of valve cell of the present invention.
The specific embodiment
Fig. 1 shows a kind of vehicle, and particularly tractor truck 1, has the pneumatic circuit 2 relevant with the lifting axis of vehicle or tractor truck 13.Except lifting axis 3, tractor truck 1 also comprises through the additional shaft of metal suspension spring suspension at the place, chassis of vehicle.For an embodiment, vehicle can comprise four axles by the metal suspension spring suspension.The axle that primary shaft in these can be turned to, and at least one axle in other is driven axle.Lifting axis 3 is particularly launched according to the operating conditions of vehicle.A kind of condition that is used to launch lifting axis is the load of vehicle.Surpass under the situation of threshold value in load, lifting axis is launched, and makes load simultaneously through being supported on the road surface by metal suspension supported by springs axle and lifting axis 3.Lifting axis 3 is suspended at the place, chassis of vehicle through lifting bellows 4 and (at least one) suspension bellow 5.When to lifting bellows 4 pressurization, lifting axis 3 moves towards the chassis, so that lifting axis 3 disengages with the road surface.Simultaneously, the suspension bellow that is positioned in the power stream between chassis and the lifting axis is deflated.Explained from make lifting axis 3 stop using towards the forced air of bellows 4,5 stream.In order to launch lifting axis 3, lifting bellows 4 is deflated, and suspension bellow 5 is inflated.Control through valve cell 6 of the present invention from bellows 4,5 with towards the forced air stream of bellows 4,5.Valve cell 6 comprises and is connected to pressurized air source, is the supply port 7 of reservoir 8 at this.And valve cell 6 comprises lifting corrugated tube port 9 that is connected to lifting bellows 4 and the suspension bellow port one 0 that is connected at least one suspension bellow 5.Shown in the schematic dotted line among Fig. 1, valve cell 6 comprises housing 11, and said housing 11 constructs port 7,9 and 10.Load dependence control cock 12, lifting bellows valve 13 and suspension bellow valve 14 are integrated in the housing 11.At this, load dependence control cock 12 can be passed through single valve gear or pass through the composite construction of a plurality of valve gears.And valve 13,14 also can be integrated in the single valve gear or form the device that separates.
Load dependence control cock 12 is transformed to the control presssure at mouth 16 places according to vehicle or the load of one of them 17 with it at this and the pressure of supplying with port 7 bonded assembly input ends 15 places.Above-mentioned dependence can be any dependence.For a possible dependence, the control presssure at mouth 16 places is proportional with load for the load 17 of given range at least.Also can be, the control presssure at mouth 16 places be corresponding with bar pressure when load 17 is lower than the threshold value of load, and when surpassing threshold value, the control presssure at mouth 16 places is corresponding or proportional with load 17 with the pressure at reservoir 8 places.For the embodiment shown in the housing 11, mouth 16 is connected with suspension bellow valve 14 with lifting bellows valve 13 via the bifurcated pilot piping 18 with the 18-1 of branch and 18-2.Control presssure in the pilot piping 18 is used as the control presssure of two valves 13,14 or controls pressure.The input end of valve 13,14 is connected with supply port 7.Valve 13,14 changes their state according to the control presssure at 18-1 of branch and 18-2 place.Valve 13,14 can be an any kind.For an embodiment, at least one valve in the valve 13,14 is a relay valve, said relay valve mouth 19,20 places produce with the 18-1 of branch, 18-2 in the relevant or proportional pressure of control presssure of bias voltage control port 21,22.The input end 23,24 of valve 13,14 is connected with supply port 7. Mouth 19,20 is connected with port 9,10.For an alternative embodiment; Valve 13 and/or valve 14 are that the 3/2-valve is (at this and in whole specification sheets; First digit, this be 3 the expression ports quantity; Have 3 ports in this expression, and second digit, this be 2 the expression switching states quantity, have two switching states in this expression).For these 3/2-valves; Under first switching state; Valve 13,14 with the pressure at the pressure at control port 21,22 places or input end 23,24 places, promptly from the transmission of pressure of reservoir 8 to mouth 19,20, wherein, under another switching state of valve 13,14; Mouth 19,20 is through valve 13,14 and atmosphere, so that relevant bellows 4,5 venting.
Valve cell 6 can be the integral type unit, maybe can be have a plurality of modules modular, and for example valve 12,13 and 14 is respectively a module, and wherein, module is assembled each other.Through assembling independent module, the corresponding pipeline of module is connected to each other.Valve 12,13,14 can be controlled through pneumatic mode and/or electronic mode.Load 17 can be delivered to valve cell 6 via mechanical connection 25 or electric port 26; Said mechanical connection 25 or electric port 26 are connected with another control unit or sensor, and said another control unit or sensor produce at least and the load of vehicle or the relevant signal of load at axle place.Load signal is derived by the CAN bus.
Fig. 2 shows a more detailed embodiment of valve cell 6 of the present invention.At this, comprise two suspension bellow 5-1,5-2 with lifting axis 3 relevant pneumatic circuits 2, said two suspension bellows have relevant suspension bellow port one 0-1,10-2.From supplying with air that port 7 gets into valve cells 6 through being integrated in the pressure confinement valve 27 the housing 11.In the downstream of pressure confinement valve 27, center culvert 28 is branched into center culvert part 28-1 and 28-2.This center culvert part 28-2 is connected with the input end 23,24 of lifting bellows valve 13 and suspension bellow valve 14.Lifting bellows valve 13 is implemented as 3/2-valve 29; Said 3/2-valve 29 switching state shown in figure 2 is connected the 28-2 of center culvert branch with lifting corrugated tube port 9; And at another switching state of 3/2-valve 29, lifting corrugated tube port 9 is connected with deflation hole 30.When control port 21 places did not have enough control presssures, spring 31 was actuated into the switching state shown in Fig. 2 with 3/2-valve 29.In Fig. 2, suspension bellow valve 14 is implemented as relay valve, and said relay valve comprises and port one 0-1 and two mouth 20-1 of 10-2 bonded assembly and 20-2.Relay valve 32 comprises independent deflation hole 33.
In Fig. 2, load dependence control cock 12 is with load-sensing valve 34, adjustable throttle structure 35, reservoir 36 and second control cock, 37 structures.At this, load-sensing valve 34 and shaft mechanical coupling are to transmit and load 17 proportional signals.The input end pressure that load-sensing valve 34 will be supplied with by the 28-1 of center culvert branch converts the pressure at mouth 38 places into pro rata according to load 17 or with load 17.Mouth 38 is connected with reservoir 36 via throttle structure 35.For the embodiment shown in Fig. 2, the mouth of reservoir 36 is connected with control port 40 with the input end 39 of second control cock 37 simultaneously, and said second control cock 37 is implemented as 3/2-valve 43 at this.At the switching state that does not have enough pressure at control port 40 places shown in Figure 2 of second control cock 37, spring 41 is biased into the switching state that mouth 16 is communicated with deflation hole 42 with second control cock 37.When control port 40 places had enough pressure, second control cock 37 was switched to second switching state (not shown among Fig. 2).At this switching state, input end 39 is connected with mouth 16.The mouth 16 of second control cock 37, be load dependence control cock 12 mouth 16 and lifting bellows valve 13 control port 21 and suspension bellow valve 14 control port 22 the two be connected.
Function according to the valve cell 6 of Fig. 2 is following: pressure confinement valve 27 remains on the pressure among the 28-1 of center culvert branch, the 28-2 in the preset range.Load-sensing valve 34 produces the pressure proportional or relevant with load 17 at mouth 38 places, said load 17 this be with load-sensing valve 38 mechanical connections spool level height.By means of throttle structure 35 and reservoir 36, when Uneven road, the pressure oscillation of the upper frequency that produces at mouth 38 places because of the quick variation with the level height of load-sensing valve 34 bonded assembly axles is smoothly fallen.Therefore, throttle structure 35 forms a kind of low-pass filter with reservoir 36.The effect of throttle structure 35 and reservoir 36 is that the vibration of upper frequency can not supply to the input end 39 and control port 40 of second control cock 37.Valve cell 6 according to Fig. 2 has two different operating states.At the related levels height of load 17 or axle when being lower than threshold value, that provide and switch 3/2-valve 43 to overcome 41 bias effect through the level and smooth insufficient pressure that acts on control port 40 places of throttle structure 35 and reservoir 36 by load-sensing valve 34.Therefore, mouth 16 is communicated with deflation hole 42 with control port 21,22.At this serviceability, the pressure of center culvert 28-2 is delivered to lifting bellows 4 through lifting bellows valve 13, so that lifting axis is remained on by the rest position of lifting.(or also for different switch pressures) simultaneously, the suspension bellow valve 14 that does not have pressure at control port 22 places is connected suspension bellow 5-1,5-2 with deflation hole 33, make suspension bellow 5-1,5-2 be deflated.
The pressure at control port 40 places of the 3/2-valve of supplying with via throttle structure 35 and reservoir 36 by load-sensing valve 34 43 surpass by the hardness of spring 41 and with the situation of the threshold value of control port 40 bonded assembly control surfaces decision under, 3/2-valve 37 switches to unshowned state among Fig. 2.At this state, the control port 21,22 of valve 13,14 is by the exert pressure from input end 39, and said pressure depends on the smoothness properties of load 17 and throttle structure 35 and reservoir 36.Relay valve 32 produces the proportional pressure of pressure with control port 22 places, promptly a kind of pressure that depends on load 17 in suspension bellow 5-1 and 5-2.Therefore, for the load that increases, suspension bellow 5-1,5-2 are by pressurization largely.Under the enough not big situation of delivery pressures load-sensing valve 34 and control port 21 places, the bias effect that the control presssure at port 21 places makes 3/2-valve 29 overcome spring 31 switches to another switching state from the switching state according to Fig. 2.Under this another switching state, lifting bellows 4 is communicated with deflation hole 30, so that lifting bellows 4 is exitted.This design with the loop 2 that lifting bellows 4 is exitted under which kind of load is relevant.This switching can be carried out when switching 3/2-valve 43 immediately, or only the pressure at control port 21 places just carries out above under the situation of threshold pressure, makes that suspension bellow 5-1 and the 5-2 proper timing before 4 venting of lifting bellows is pressurized.Reservoir 36 can have the volume of 100-200cm3.
For the another embodiment of the present invention shown in Fig. 3, pressure confinement valve 27 is not integrated in the center culvert 28, but is integrated among the 28-1 of center culvert branch, makes inhibitor valve 27 influences that are not stressed of pressure among the 28-2 of center culvert branch.In this case, load dependence control cock 12 with the cooresponding interconnective load-sensing valve of the embodiment of Fig. 2 34, adjustable throttle structure 35, reservoir 36 and second control cock, 37 structures.Yet at this, second control cock 37 makes up through 5/2-valve 44, and the embodiment of said 5/2-valve 44 and Fig. 2 switches between two states through the pressure at control port 40 places similarly.At the state shown in Fig. 3, promptly when load 17 is lower than threshold value, thereby the first mouth 16-1 of 5/2-valve 44 is connected with the mouth 38 of input end 39 with reservoir 36, throttle structure 35 and load-sensing valve 34.Another mouth 16-2 of 5/2-valve 44 is connected with deflation hole 45.Mouth 16-1 is connected with the control port 21 of lifting bellows valve 13, makes that control port 21 quilts are with load dependence exert pressure at the switching state that illustrates of second control cock 37.Mouth 16-2 is connected with the control port 22 of the suspension bellow valve 14 of exitting via deflation hole 45.At this switching state, lifting bellows 4 is via 13 pressurizations of lifting bellows valve, and suspension bellow 5-1 and 5-2 are via 14 venting of suspension bellow valve.Increase under the situation with the load dependence pressure increase at control port 40 places in load 17, the bias effect that 5/2-valve 44 overcomes spring 41 switches to unshowned state among Fig. 3.At this switching state, mouth 16-1 is communicated with another deflation hole 46, and mouth 16-2 is connected with input end 39.Therefore, at this switching state, control port 21 is deflated, thereby makes lifting bellows 4 be communicated with deflation hole.The control port 22 of suspension bellow valve 14 is inflated with load dependence control presssure, thereby makes suspension bellow 5-1 and 5-2 inflation.Therefore, lifting axis 3 is activated.
For embodiment shown in Figure 3, lifting bellows valve 13 is implemented as relay valve 32,47 with suspension bellow valve 14.In this case, input end 23,24 is via center culvert 28 and the 28-2 of center culvert branch and supply port 7 and reservoir 8 direct connections.
Feeling of stress side valve 34 can be any this feeling of stress side valve.Especially, use a kind of like this feeling of stress side valve 34, wherein, delivery pressure 38 is only relevant with load 17, and irrelevant with input pressure, also please referring to the embodiment of Figure 19.
As shown in Figure 3, the spring 41 of second control cock 37 can be suitable for changing the switch pressure of second control cock 37.
Embodiment shown in Figure 4 is corresponding with the embodiment shown in Fig. 2 generally.Yet,, pressure confinement valve 27 is not set at this.And at this, second control cock 37 also is equipped with adjustable spring 41, is used to change the switch pressure of second control cock 37.
Embodiment shown in Fig. 5 is relevant with the embodiment shown in Fig. 4 generally.Yet at this, via 9 inflations of lifting corrugated tube port and venting, in this embodiment, said lifting bellows valve 13 is the 3/2-valve through lifting bellows valve 13 for two lifting bellows 4-1,4-2.And load dependence control cock 12 is not configured with throttle structure 35 and reservoir 36, and the load-sensing valve 34 and second control cock 37 are only arranged, and at this, said second control cock 37 is a 3/2-valve 43.In the embodiment show in figure 5; Deflation hole 30,33 is connected with integrated residual pressure valve 49 through common bleeder line, said residual pressure valve 49 to suspension bellow 5-1,5-2 and lifting bellows 4-1, guarantee Min. pressure when 4-2 exits.Bleeder line 48 is connected with the deflation hole that comprises noisekiller 51 50 of housing 11.
For embodiment shown in Figure 6, load dependence control cock 12 is only with load-sensing valve 34 structures.At this, the mouth 16 of load dependence control cock 12 is corresponding with the mouth 38 of the load-sensing valve 34 of fwd embodiment.Mouth 16 is connected with the control port 53 of valve gear 54 through the pilot piping 18 with integrated adjustable throttle structure 52.Except pilot piping 18, the mouth 16 of feeling of stress side valve 34 is connected with the feed pipe 55 with load dependence forced air.Valve gear 54 is 5/2-valves 56, and this 5/2-valve 56 has and input end of feed pipe 55 bonded assemblys, two deflation holes and two and suspension bellow 5-1,5-2 and lifting bellows 4 bonded assembly mouths 19,20.The spring 57 of 5/2-valve is adjustable.For the pressure in the pilot piping that is lower than threshold pressure 18, promptly for the load that is lower than threshold value load 17, the 5/2-valve is in switching position shown in Figure 6, and wherein, feed pipe 55 is connected with lifting bellows 4 with mouth 19.Mouth 20 is communicated with deflation hole with suspension bellow 5-1,5-2, to be used to make suspension bellow 5-1,5-2 venting.This switching state is corresponding with the lifting axis of stopping using.For bigger load 17, that is, for the pressure at control port 53 places of 5/2-valve 56 situation greater than threshold pressure, the 5/2-valve switches to second state.At this second state relevant with the lifting axis of launching 3, mouth 20 is connected with feed pipe with suspension bellow 5-1,5-2, so that suspension bellow 5-1,5-2 inflation, and mouth 19 is connected with deflation hole, so that lifting bellows 4 is exitted.For this embodiment, valve gear 54 makes up lifting bellows valve 13 and suspension bellow pipe 14 with single valve gear.
Embodiment shown in Fig. 7 generally with Fig. 4 in embodiment corresponding.Yet in this case, second control cock 37 that is implemented as 3/2-valve 43 comprises additional electrical actuator 58.Therefore, second control cock 37 is electromagnetic valves, makes it pass through air operated control port 40 and electromagnetic actuators 58 equal may command second control cock 37.Especially, the electric actuation of actuator 58 produces power or Pneumatic pressure, and the switching state shown in said power or Pneumatic pressure and Fig. 7 is bias voltage 3/2-valve 43 on the contrary.Be higher than in load 17 under the situation of threshold value; Promptly the control presssure at control port 40 places is enough to second control cock 37 is switched under the situation of unshowned second switching state among Fig. 7, and the actuating of actuator 58 can make second control cock 37 transform to the switching state shown in Fig. 7.Under the driving conditions that this can be used under the situation of driving conditions of vehicle backward and/or the tractive force that increases when being used for also having bigger load at other places except lifting axis receives publicity.Actuator 58 is through 67 controls of appropriate control unit, and said control unit 67 can be integrated in the housing 11 and maybe can be positioned at outside the valve cell 6, but can communicate by letter with valve cell 6 via suitable port or CAN bus.
Fig. 8 shows the similar embodiment with the embodiment of Fig. 7.Yet at this, second control cock 37 comprises another actuator 59 or the electromagnetic valve with the directive effect opposite with actuator 58, so it is in identical direction with control port 40.(also can be that the actuator 58,59 that is used for both direction makes up through single bidirectional actuator.) electric actuation through actuator 59, also can launch lifting axis 3 under with the situation that second control cock 37 is switched to unshowned switching state among Fig. 8 in the insufficient pressure at load 17 and control port 40 places.Therefore, control unit can be launched lifting axis via actuator 59 when needed.
For generally with the embodiment of cooresponding Fig. 9 of embodiment of Fig. 8, the pneumatic actuator that two actuators 58,59 that activated and form electromagnetic actuators by the mode with electricity have been had control port 60,61 substitutes.Pressurized with the control port that second control cock 37 transformed to unshowned state among Fig. 9 61 through control cock 62 controls, said control cock 62 is the 3/2-valve that is implemented as electromagnetic valve at this.At the state that is not given energy shown in Fig. 9; Control cock 62 is communicated with control port 61 with deflation hole; And be given the state of energy at another; Control cock 62 is connected control port 61 with the 28-2 of center culvert branch, make at this state, produces the power that second control cock 32 is biased into another state from state shown in Figure 9.The pressure at control port 60 places is through another control cock 63 controls.At this, control cock 63 is for being implemented as the 3/2-valve of electromagnetic valve.Not to the state shown in Fig. 9 of magnet coil power supply; Control cock 63 makes control port 60 venting; And at another switching state to the magnet coil power supply; Control port 60 is connected with reservoir 63 or the 28-1 of center culvert branch, thereby makes second control cock 37 transform to the switching state shown in Fig. 9 again.Through via control unit or external control unit controls control cock 62,63 as the part of valve cell 6, can be through the switching state that depends on the pneumatically actuated of load-sensing valve 34 and control second control cock 37 through the electric actuation of control cock 63,62.For this embodiment, load dependence control cock 12 is with load-sensing valve 34, throttle structure 35, reservoir 36, second control cock 37 and control cock 62,63 structures, and wherein, control cock 62,63 influences the pressure at mouth 16 places of second control cock 37.
Figure 10 shows the similar embodiment with the embodiment shown in Fig. 4.Yet at this, center culvert 28 comprises pressure confinement valve 27.Yet the control port 40 of second control cock 37 directly is not connected with reservoir 36.On the contrary, control cock 64 is integrated in the connecting line between control port 40 and the reservoir 36.Control cock 64 is 3/2-valves, is electromagnetic valve at this.At the state that is not given energy shown in Figure 10, control cock 64 is connected control port 40 with reservoir 36, and is being given under the state of energy, and control cock 64 is communicated with port 40 with deflation hole.Therefore, at the switching state that is not given energy of control cock 64, and produce the control presssure of the control port 21,22 that is used for lifting bellows valve 13 and suspension bellow valve 14, to be used to activate lifting axis for enough load 17, the second control cock 37.Yet, not the serviceability of being concerned about at the lifting axis that activated, can be with the mode actuation control valve 64 of electricity.Through this electric actuation, control cock 64 switches to unshowned switching state among Figure 10, makes the control port 40 of second control cock 37 be deflated.Correspondingly, second control cock 37 also changes to its switching state and the cooresponding switching state of lifting axis of stopping using.Under launching of lifting axis afterwards is necessary situation, to stop using through the electronics of control cock 64, lifting axis 3 is activated once more.Stopping using of this electronic control type of lifting axis can be when detecting or predicting the vehicle backward and/or carry out when increasing the tractive force of vehicle.For the embodiment of Figure 10, control cock 64 constitutes the part of load dependence control cock 12.
Figure 11-18 shows the distinct methods that is used to realize valve cell 6, particularly load dependence control cock 12, lifting bellows valve 13 and suspension bellow valve 14.At this, be positioned within the valve cell 6 or outside the level height or the load of sensor 65 measurement axis.Sensor 65 can be the sensor of any kind.Especially, sensor 65 be sensitive axis level height displacement pickup or measure the force gauge of load directly or indirectly.The signal of the sensor 65 relevant with load supplies to electronic control unit 67 via signal port 66, and said electronic control unit 67 is integrated in the housing 11 of valve cell 6.For embodiment shown in Figure 11, load dependence control cock 12 only constitutes through two control cock 68,69, and said two control cock 68,69 are to be implemented as the 3/2-valve 70,71 of electromagnetic valve and by electronic control unit 67 controls at this.The input end of control cock 68,69 is supplied to forced air via the 28-1 of center culvert branch, 28-3.And control cock 68,69 comprises a deflation hole respectively or is connected to the pipeline of common deflation hole as shown in Figure 5.The mouth 16-1 of control cock 68,69 is connected with the relative control port 72,73 of valve gear 54 with 16-2, and said valve gear 54 constitutes lifting bellows valve 13 and suspension bellow valve 14.For embodiment shown in Figure 11, valve gear 54 is made up by the 6/3-valve.At the middle switching state of the valve gear 54 shown in the Figure 11 that does not have pressurized control port 73,72 or identical ground these ports 72,73 that pressurize, the output port 20-1 of valve gear 54,20-2 are connected with suspension bellow 5-1,5-2 via suspension bellow port one 0-1,10-2.In valve gear 54, mouth 20-1,20-2 connect through a restriction, and said restriction particularly reduces or suppress the exchange of the forced air between suspension bellow 5-1, the 5-2 when turning driving.Blocked at the midway location of 6/3-valve 74 via lifting corrugated tube port 9 with the mouth 19 of lifting bellows 4 bonded assembly valve gears 54.
During greater than the pneumatically actuated power of control port 72,6/3-valve 74 transforms to right cut and changes state in the pneumatically actuated power of control port 73.At this switching state, mouth 20-1,20-2 are communicated with deflation hole through the 6/3-valve, make suspension bellow 5-1,5-2 exit.Mouth 19 is connected with the 28-2 of center culvert branch through the 6/3-valve at this switching state, makes that lifting bellows 4 is pressurized.Therefore, this switching state of 6/3-valve is corresponding with the lifting axis of stopping using.
When comparing with pressurized control port 72 more with control port 73, the 6/3-valve transforms to left cut and changes state.At this switching state, mouth 20-1,20-2 are connected with the 28-2 of center culvert branch, make suspension bellow 5-1,5-2 be inflated.On the contrary, the mouth 19 and the atmosphere of 6/3-valve 74 make lifting bellows 4 exit.
Therefore, by means of the control port of electronic control unit 67 control control cock 68,69, can
-place throttle structure between these two suspension bellow 5-1, the 5-2 to keep the pressure condition of lifting bellows 4 and suspension bellow 5-1,5-2 in the middle switching state utilization of valve 6/3-valve,
-valve gear 54 switched to the inactive cooresponding right cut of lifting axis 3 change state, and
-valve gear 54 switched to the cooresponding left cut of launching of lifting axis 3 change state.
Therefore, based on by the load that sensed or level height or based on aforesaid other conditions, optionally launch and inactive lifting axis 3.And in order to control the pressure among suspension bellow 5-1, the 5-2, the pressure in these suspension bellows 5 is through pressure sensor 75 sensings.This pressure sensor 75 can be positioned at outside the valve cell 6, and wherein, housing 11 comprises the additional signal port 76 that is used for the signal of sensor 75 is delivered to electronic control unit 67.Yet, pressure sensor 75 is integrated in the housing 11 and the pressure in sensing mouth 20-1,20-2 downstream.
Embodiment among embodiment shown in Figure 12 and Figure 11 is similar.Yet, at this, the control port 73,72 of control cock 68,69 control cock devices 54, said valve gear 54 is a 4/3-valve 77 at this, mainly is responsible for making suspension bellow 5-1,5-2 inflation and venting.When comparing with the 6/3-valve 74 of Figure 11, the 4/3-valve does not comprise in two deflation holes, and does not comprise the mouth 19 that is used for lifting bellows 4.About three control of position to valve gear 54, mouth 20-1,20-2 are connected to each other via throttle structure or are corresponding with the valve gear 54 of Figure 11 with the connection of deflation hole or the 28-2 of center culvert branch.For this embodiment, valve gear 54 constructs suspension bellow valve 14, and load dependence control cock 12 is made up by control cock 68,69.According to Figure 12, lifting bellows valve 13 is made up by 3/2-valve 78.Internal duct between mouth 20 and the suspension bellow port one 0 is branched to the control port 80 bonded assembly pilot piping 79 with 3/2-valve 78.The input end of 3/2-valve 78 is connected with the 28-4 of center culvert branch.And 3/2-valve 78 comprises deflation hole 81.The mouth 148 of 3/2-valve 78 is connected with lifting corrugated tube port 9.At the switching state shown in Figure 12, the 3/2-valve is connected mouth 148 with the 28-4 of center culvert branch, and at another switching state of the control port with pressurization 80, mouth 148 is communicated with deflation hole 81, thereby makes 4 venting of lifting bellows.Valve cell 6 according to Figure 12 acts on as follows: under the situation of the mouth 20 through controlling control cock 68,69 pressurizing valve devices 54 suitably, suspension bellow 5-1,5-2 are pressurized.Simultaneously, via pilot piping 79, the control port of 3/2-valve 78 80 is pressurized and make 4 venting of lifting bellows.Correspondingly, lifting axis is activated.On the contrary, when making mouth 20 with suspension bellow 5-1,5-2 venting, pilot piping 79 and 80 also is deflated, and makes that lifting bellows 4 is pressurized from the 28-4 of center culvert branch via 3/2-valve 78.
For embodiment shown in Figure 13, level height or load transducer 65 are integrated in the housing 11 of valve cell 6 with pressure sensor 75.At this, two control cock 68,69 are corresponding with aforesaid control cock 68,69 at their design aspect, and they are connected with the 28-1 of center culvert branch, 28-3, and they are through control unit 67 controls.Yet the mouth 16-1 of control cock 68 is connected with the control port 82 of suspension bellow valve 14, and said suspension bellow valve 14 is a 2/2-valve 83 at this.The mouth 16-2 of control cock 69 is connected with the control port 84 of lifting bellows valve 13, and said lifting bellows valve 13 is a 5/2-valve 85 at this.At the switching state shown in Figure 13,5/2-valve 85 is communicated with lifting corrugated tube port 9 with deflation hole, and the 28-2 of center culvert branch is connected with the mouth 86 of 5/2-valve 85.On the contrary, another switching state that when pressurized control port 84 time, is reached, lifting corrugated tube port 9 is connected with the 28-2 of center culvert branch through 5/2-valve 85, and mouth 86 is communicated with deflation hole.Correspondingly, at the switching state shown in Figure 13, lifting bellows 4 is deflated, and at another switching state, lifting bellows 4 is inflated through the joint construction with reservoir 8.The mouth 86 of 5/2-valve 85 is connected with the input end 87 of 2/2-valve 83, and the mouth of 2/2-valve 83 and pressure sensor 75 and suspension bellow port one 0 the two be connected.Switching state at the 2/2-valve 83 shown in Figure 13; Suspension bellow port one 0 quilt blocks with input end 87; And for via control cock 68 pressurized control ports 82, suspension bellow port one 0 is connected with input end 87, also promptly is connected with the mouth 86 of 5/2-valve 85.Correspondingly, the pressure at suspension bellow port one 0 place is relevant with switching state 2/2-valve 83 and 5/2-valve 85.At the switching state shown in Figure 13; The pressure that 2/2-valve 83 keeps among suspension bellow 5-1, the 5-2; And under another switching state, the 2/2-valve provides the selection that changes the pressure among suspension bellow 5-1, the 5-2 through control 5/2-valve 85: in the position shown in Figure 13, the pressure among suspension bellow 5-1, the 5-2 increases via the 28-2 of center culvert branch; And at another switching state of 5/2-valve 85, suspension bellow 5-1,5-2 are deflated.At this, the minimum pressure among suspension bellow 5-1, the 5-2 can be through being guaranteed via pressure sensor 75 pressure sensors.Detect under the situation that pressure is lower than a ultimate pressure (at this for 2bar) at electronic control unit 67; Electronic control unit 67 transforms to the switching state that gets clogged via control cock 68 with 2/2-valve 83, further reduces to avoid the pressure among suspension bellow 5-1, the 5-2.
Figure 14 shows the quite similar embodiment with the embodiment of Figure 13.Yet at this, electronic control unit 67 and sensor 65 are positioned at outside the housing 11 of valve cell 6 with pressure sensor 75.Electronic control unit 67 is communicated by letter with valve cell 6 via electric port one 49.At this; The order of 5/2-valve 85 and 2/2-valve 83 is changed; Make the 2/2-valve of controlling through control cock 69 83 have and the 28-2 of center culvert branch bonded assembly input end, and the mouth of this 2/2-valve 83 is connected, and supplies with forced air to give this valve with the input end of 5/2-valve 85.In this case, a mouth of 5/2-valve 85 directly links to each other with suspension bellow port one 0, and another mouth directly links to each other with lifting corrugated tube port 9.Switching state at the 5/2-valve 85 shown in Figure 14; Lifting bellows 4 is deflated; And at another switching state, lifting bellows 4 is connected with the 2/2-valve, feasible state according to the 2/2-valve; Lifting bellows 4 or get clogged (making pressure be maintained) or be connected with center culvert 28-2 is so that 4 inflations of lifting bellows.The switching state of unshowned 5/2-valve in Figure 14, suspension bellow 5-1,5-2 are deflated.On the contrary; Pressurized state at the control port of the 5/2-valve 85 shown in Figure 14; Suspension bellow port one 0 is connected with 2/2-valve 83 via 5/2-valve 85; Make state according to 2/2-valve 83, suspension bellow 5-1,5-2 or get clogged or is connected with the 28-2 of center culvert branch so that suspension bellow 5-1,5-2 inflate.
For embodiment shown in Figure 15, suspension bellow valve 14 is 3/2-valve 88 structures with first valve, at this, and said first valve is pneumatically controlled through control cock 68.The mouth of 3/2-valve 88 is connected with suspension bellow 5-1, the 5-2 of the not homonymy of vehicle via suspension bellow port one 0-1,10-2.At the not pressurized state of the control port of 3/2-valve 88, promptly at the state shown in Figure 15,3/2-valve 88 connects two suspension bellow 5-1,5-2 via the throttle structure that is integrated in the 3/2-valve 88.At another switching state, promptly for the ports that pressurize via control cock 68, suspension bellow port one 0-1,10-2 are connected with the input end of 3/2-valve.The input end of 3/2-valve is connected with the mouth of 3/2-valve 89, and the part of lifting bellows valve 14 pneumatically controlled and also constitute by said 3/2-valve 89 through control cock 69.At not pressurized switching state, that is, at the state shown in Figure 15,3/2-valve 89 is communicated with mouth with deflation hole.Correspondingly, the 3/2-valve 89 that do not pressurize in order to pressurize 3/2-valve 88, suspension bellow port one 0-1,10-2 are deflated.At the pressurized switching state of 3/2-valve 89, mouth is connected with the 28-2 of center culvert branch, makes that suspension bellow 5-1,5-2 are inflated for pressurized 3/2-valve 88 and pressurized 3/2-valve 89.
For the embodiment shown in Figure 15, lifting bellows valve 13 makes up through the 3/2-valve 90 of air operated control.The input end of 3/2-valve 90 is connected with the 28-4 of center culvert branch, and the mouth of 3/2-valve 90 is connected with lifting corrugated tube port 9.Thereby the control port 91 of 3/2-valve 90 is connected with the mouth of 3/2-valve 88 with a pipeline in the pipeline that leads to suspension bellow port one 0-1,10-2.Do not have enough pressure at suspension bellow 5-1,5-2 3/2-valve 90 is switched among Figure 15 under the unshowned state, lifting bellows 4 is inflated from the 28-4 of center culvert branch via 3/2-valve 90.Yet under the situation of pressurization suspension bellow port one 0-1,10-2, the pressure that acts on control port 91 places switches to unshowned switching state among Figure 15 with 3/2-valve 90.At this switching state, lifting bellows 4 is deflated via the deflation hole of 3/2-valve 90.
Figure 16 shows and is used for through the 28-2 of center culvert branch being connected another embodiment that makes up suspension bellow valve 14 with suspension bellow port one 0 via the 3/2-valve 92 of controlled valve 69 controls and the 2/2-valve 93 of controlled valve 68 controls.At the not pressurized switching state of the 2/2-valve 93 shown in Figure 16, the pressure among suspension bellow 5-1, the 5-2 is owing to blocked state is maintained.Yet when the control port of pressurization 2/2-valve 93, valve is switched to another state, and at this another state, suspension bellow port one 0 is connected via the mouth of 2/2-valve 93 with 3/2-valve 92.At the not pressurized state of 3/2-valve 92, promptly at the state shown in Figure 16, and for the coupled condition of 2/2-valve 93, suspension bellow port one 0 is deflated via the deflation hole of 3/2-valve 92.For 3/2-valve 92 is switched to another state, can inflate suspension bellow port one 0 from the 28-2 of center culvert branch via valve 92,93.
For the embodiment shown in Figure 16, lifting bellows valve 13 makes up through 3/2-valve 94.3/2-valve through solenoid control is a 3/2-valve 95 at this, and said electromagnetic valve is through electronic control unit 67 controls.The input end of 3/2-valve 94,95 all is connected with the 28-4 of center culvert branch, and the mouth of 3/2-valve 95 is connected with the control port of 3/2-valve 94, and the mouth of 3/2-valve 94 is connected with lifting corrugated tube port 9.The actuator that starts 3/2-valve 95 can change to another state (control port of 3/2-valve 94 is inflated from the 28-4 of center culvert branch) from the state shown in Figure 16 (control port of 3/2-valve 94 is deflated) with state.For not controlled port by the 3/2-valve 94 of pressurization sufficiently; At the state shown in Figure 16; 3/2-valve 94 is connected lifting corrugated tube port 9 with deflation hole; And having pressurized another state of controlling port, lifting corrugated tube port 9 is connected with the 28-4 of center culvert branch, so that lifting bellows 4 is put on the air.Through electric control control cock respectively 68,69 with also constitute the 3/2-valve 95 of control cock, both pressure states of may command suspension bellow 5-1,5-2 and lifting bellows 4.For this embodiment, load dependence valve 12 is with control cock 68,69 and 95 structures.
Embodiment shown in Figure 17 is corresponding with the embodiment shown in Figure 16 generally, is integrated with electronic control unit 67, control cock 68,69 identically and has the bellows valve 14 that suspends of valve 92,93.Yet at this, lifting bellows valve 13 is through being connected structure with the 28-4 of center culvert branch with lifting corrugated tube port 9 via the combination of 3/2-valve 96 and 2/2-valve 97 (but also transpose).Valve 96,97 is respectively through control cock 98,99 controls; Said control cock 98,99 is the electromagnetic valve through electronic control unit 67 controls, and be configured for according to the control signal from electronic control unit 67 provide zero control presssure or with the 3/2-valve of the control presssure of reservoir pressure correlation.According to the switching state of the switching state of control cock 98,99 and the valve 96,97 that is caused, can block lifting corrugated tube port 9, lifting corrugated tube port 9 is connected with valve 96 and makes 9 venting of lifting corrugated tube port or inflation corresponding to the state of valve 96.The embodiment that illustrates with four control cock 68,69,98,99 provides the abundant control ability of obstruction, inflation and the venting of controlling suspension bellow 5 and lifting bellows 4 individually.
Figure 18 shows another embodiment of the present invention, wherein, lifting bellows valve 13 have with Figure 17 in the cooresponding design of design.And the design of suspension bellow valve 14 and Figure 17's is also similar.Yet for the embodiment shown in Figure 18, lifting bellows 5-1 and 5-2 are respectively through independent loop control.Correspondingly, it is related with suspension bellow port one 0-1 to be positioned at the 2/2-valve 93-1 in 3/2-valve 92 downstream.Also be connected with suspension bellow port one 0-2, respectively suspension bellow 5-2 is inflated, blocks or venting with another 2/2-valve of mouth bonded assembly 93-2 of 3/2-valve 92.Correspondingly, need additional control cock 100 to control additional 2/2-valve 93-2.
Figure 19 shows the more detailed view with the similar valve cell 6 of valve cell shown in Fig. 76.Supply with port 7 and be connected with center culvert 28, said center culvert along continuous straight runs in Figure 19 extends through housing 11 and upwards direction extension of edge therefrom to the right side of Fig. 9.Center culvert 28 is connected with hole 101 fluids, and said hole 101 is connected with valve chamber 102.Valve chamber 12 comprises valve seat 103, and said valve seat 103 limits out the passage of another chamber 104.At the state shown in Figure 19, this passage is through valve body 105 sealings, and said valve body 105 is abutted against valve seat 103 extruding by valve spring 106.Under the situation that the load of the axle of vehicle increases, bar 107 moves in the upward direction.Motion-related for enough big load and bar 107; The front surface extruding valve body 105 of bar 107; Bias voltage to valve spring 106 is increased, thereby open passage and allow forced air to flow into chamber 104 via center culvert 28 through hole 101 and valve chamber 102 from supplying with port 7.For embodiment shown in Figure 19, the motion of bar 107 is caused that by eccentric stiffener 108 said eccentric stiffener 108 is rotated corresponding to the variation of the level height of the axle of vehicle.Valve seat 103 makes up through the piston 145 of confinement cells 104, and is supported by spring 146.When the pressure in chamber 104 (with reservoir 36) increased, piston 145 moved under the bias effect of the increase of spring 146 in the upward direction, and the passage between closed valve 105 and the valve seat 103.For this embodiment, do not need pressure confinement valve-delivery pressure only on little degree, to receive the influence of the variation of input pressure.For this reason, the surface-limited of valve chamber 102 is selected as little.Reservoir 36 is connected through the path 10 9 that constitutes throttle structure 35 with chamber 104.
In second control cock 37, the pressure of reservoir 36 acts on the following ring surface 111 of piston 110.Piston 110 is by spring 112 bias voltage in a downward direction.In the position of the piston shown in Figure 19 110, packing element 113 sealing from be configured in ring surface 111 belows and with the passage of reservoir bonded assembly chambers 36 to control cabin 114.In order to increase the pressure in the reservoir 36, piston 110 moves under the bias effect of the increase of spring 112 in the upward direction.For predetermined miles of relative movement, packing element 113 becomes invalid, thereby discharges from reservoir 36 to control cabin 114 the passage that is used for forced air.On the contrary, the position of the piston 110 during for effective seal element 113 these passages of sealing, control cabin 114 is communicated with deflation hole 117 via passage 115,116.For the identical miles of relative movement of piston 110, this exhaust is communicated with closes through another packing element 147, and packing element 113 becomes invalid under the situation of this identical miles of relative movement.Control cabin 114 is connected with pilot piping 118, and said pilot piping 118 is used for to lifting bellows valve 13, is 3/2-valve 29 and suspension bellow valve 14, supplies with control presssures at this for relay valve 32, corresponding to the pilot piping among Fig. 1 18 at this.
In lifting bellows valve 13, valve body 119 is compressed in valve seat 120 places, thereby, be closed to the connection of deflation hole 121.The bias effect that valve seat 120 can overcome spring 122 moves along downward direction.In the position that illustrates, the passage between the output chamber 123 of valve body 119 restriction center culvert 28 and lifting bellows valve 13.The output chamber is connected with mouth 19, and said mouth is connected with lifting corrugated tube port 9.Another spring 124 pushes valve body 119 relative valve seats 120 in a downward direction, and under the bias effect of spring 122, pushes valve seat 120 in a downward direction.Valve body 119 is connected with piston 125, and said piston 125 has the following ring surface 126 of restriction control cabin 127.Control cabin 127 for good and all is connected with pilot piping 118.Increased pressure in the pilot piping 118 makes piston 125 and valve body 119 move and the bias effect of increase spring 124 in the upward direction.Valve seat 120 moves with piston 125 in the upward direction.Valve seat 120 contacts with the valve seat 128 that is fixed on housing 11 places.Being connected between output chamber 123 and the center culvert 28 closed in contact between valve seat 120 and the valve seat 128.Piston 125 being moved further in the upward direction makes valve body 119 separate with valve seat 120, thereby forms the passage from deflation hole 121 to output chamber 123, makes mouth 19 be deflated.
The suspension bellow valve that is made up by relay valve 32 comprises relay piston 129.The last ring surface 130 of relay piston 129 is by the air pressurized from pilot piping 118.In the position that illustrates of this relay piston 129, pilot piping 118 is not pressurized.Be connected with deflation hole 134 with passage between the valve seat 133 through being formed on the valve body 132 that is fixed in relay piston 129 places in this position of relay piston 129 and suspension bellow port one 0 bonded assembly output chamber 131.When the pressure at ring surface 130 places that increase pilot piping 118 places and relay piston 129, the relay piston 129 that has valve body 132 is mobile in a downward direction.Valve body 132 is compressed on the valve seat 133.Valve body 132 forms sealing with valve seat 133 and is connected, thus the above-mentioned passage of sealing from output chamber 132 to deflation hole 134.For relay piston 129 being moved further in a downward direction, valve seat overcome in a downward direction spring 135 bias effect move.This moment is at valve seat 133 and be supported between the valve body 136 at housing 11 places and form passage.This passage makes pressurized air to get into output chamber 131 and suspension bellow port one 0 from center culvert 28.
Output chamber 131 and 137 pneumatic connections of chamber, said chamber 137 is by following ring surface 138 restrictions of relay piston 129.When the pressure of output in the chamber 131 increased, when promptly the pressure at following ring surface 138 places at relay piston 129 places increased, the power that causes at ring surface 138 places was just offset the power that the control presssure by ring surface 130 places causes more and more, and making provides relay function.
Usually, the pressure in the pilot piping 118 is relevant with the pressure in the reservoir 38.Yet valve cell 6 comprises into the electromagnetic valve of the form of 3/2-valve 139.A port one 40 is connected with center culvert 28, and another port one 41 forms deflation holes, and the 3rd port one 42 is connected with the chamber 143 that upper surface 144 by piston 110 limits.In the position of 3/2-valve 139 shown in Figure 19, port one 41 is connected with chamber 143.Correspondingly, do not produce power at 144 places, surface of piston 110.Yet when 3/2-valve 139 is switched to another state, valve 139 is connected chamber 143 with center culvert 28.Therefore, produce power at surperficial 144 places, said power is extrusion piston 110 in a downward direction.When not activating 3/2-valve 139 under pilot piping 118 and the reservoir 36 bonded assembly situation, the actuating of 3/2-valve 139 makes being connected between reservoir 36 and the pilot piping 118 be interrupted, and pilot piping 118 is communicated with deflation hole 117.Therefore,, surpass the lifting axis of also can stopping using under the situation of predetermined threshold, make that just often lifting axis is activated in the load of vehicle by means of 3/2-valve 129.
Person of skill in the art will appreciate that, the control policy of the embodiment shown in can changing and/or use have the switching state put upside down shown in valve.
Reference numerals list
1 tractor truck
2 loops
3 lifting axis
4 lifting bellowss
5 suspension bellows
6 valve cells
7 supply with port
8 reservoirs
9 lifting corrugated tube ports
10 suspension bellow ports
11 housings
12 load dependence control cock
13 lifting bellows valves
14 suspension bellow valves
15 input ends
16 mouths
17 load
18 pilot piping
19 mouths
20 mouths
21 control ports
22 control ports
23 input ends
24 input ends
25 mechanical connections
26 electric ports
27 pressure confinement valves
28 center culvert
29 3/2-valves
30 deflation holes
31 springs
32 relay valves
33 deflation holes
34 load-sensing valves
35 throttle structures
36 reservoirs
37 second control cock
38 mouths
39 input ends
40 control ports
41 springs
42 deflation holes
43 3/2-valves
44 5/2-valves
45 deflation holes
46 deflation holes
47 relay valves
48 bleeder lines
49 residual pressure valves
50 deflation holes
51 noisekillers
52 throttle structures
53 control ports
54 valve gears
55 feed pipes
56 5/2-valves
57 springs
58 actuators
59 actuators
60 control ports
61 control ports
62 control cock
63 control cock
64 control cock
65 sensors
66 signal ports
67 electronic control units
68 control cock
69 control cock
70 3/2-valves
71 3/2-valves
72 control ports
73 control ports
74 6/3-valves
75 pressure sensors
76 signal ports
77 4/3-valves
78 3/2-valves
79 pilot piping
80 control ports
81 deflation holes
82 control ports
83 2/2-valves
84 control ports
85 5/2-valves
86 mouths
87 input ends
88 3/2-valves
89 3/2-valves
90 3/2-valves
91 control ports
92 3/2-valves
93 2/2-valves
94 3/2-valves
95 3/2-valves
96 3/2-valves
97 2/2-valves
98 control cock
99 control cock
100 control cock
101 holes
102 valve chambers
103 valve seats
Room 104
105 valve bodies
106 valve springs
107 bars
108 eccentric stiffeners
109 passages
110 pistons
111 ring surfaces
112 springs
113 packing elements
114 control cabins
115 passages
116 passages
117 deflation holes
118 pilot piping
119 valve bodies
120 valve seats
121 deflation holes
122 springs
Output chambers 123
124 springs
125 pistons
126 ring surfaces
127 control cabins
128 valve seats
129 relay valves
130 ring surfaces
Output chambers 131
132 valve bodies
133 valve seats
134 deflation holes
135 springs
136 valve bodies
Room 137
138 ring surfaces
139 3/2-valves
140 ports
141 ports
142 ports
Room 143
144 surfaces
145 pistons
146 springs
147 packing elements
148 mouths
149 electric ports

Claims (23)

1. valve cell (2) of vehicle that is used to have the axle that is suspended at metal suspension spring place; Said valve cell (2) comprises housing (11); Said housing have the feed pipe that is used to be connected to pressurized air source supply port (7), be used for lifting axis (3) lifting bellows (4) lifting corrugated tube port (9) and be used for the suspension bellow port (10) of the suspension bellow (5) of lifting axis (3), said housing (11) comprises:
-be used to control at least one lifting bellows valve (13) of the pressure that lifting corrugated tube port (9) locates,
-be used to control at least one suspension bellow valve (14) of the pressure that suspension bellow port (10) locates, and
-pneumatically control at least one load dependence control cock (12) of lifting bellows valve (13) and/or suspension bellow valve (14).
2. valve cell as claimed in claim 1 (2) is characterized in that, it comprises reservoir (36).
3. according to claim 1 or claim 2 valve cell (2) is characterized in that load dependence control cock (12) comprises mechanically actuated load-sensing valve (34).
4. according to claim 1 or claim 2 valve cell (2) is characterized in that load dependence control cock (12) comprises electromagnetic valve, said electromagnetic valve according to the electric signal of the sensor (65) of the load of senses vehicle through electronic control unit (67) Be Controlled.
5. like arbitrary described valve cell (2) among the claim 1-4, it is characterized in that load dependence control cock (12) is constructed with load-sensing valve (34) with through second control cock (37) of load-sensing valve (34) air operated control.
6. valve cell as claimed in claim 5 (2) is characterized in that, the mouth of load-sensing valve (34) is connected with the control port (40) of second control cock (37) and the input end (39) of second control cock (37).
7. like arbitrary described valve cell (2) among the claim 1-6, it is characterized in that input port (7) is connected with load dependence control cock (12) via pressure confinement valve (27).
8. like arbitrary described valve cell (2) among the claim 1-7, it is characterized in that second control cock (37) is 3/2-valve (43).
9. like arbitrary described valve cell (2) among the claim 1-8, it is characterized in that lifting bellows valve (13) and/or suspension bellow valve (14) are 3/2-valve (29).
10. like arbitrary described valve cell (2) among the claim 1-9, it is characterized in that lifting bellows valve (13) and/or suspension bellow valve (14) are relay valve (32).
11. like arbitrary described valve cell (2) among the claim 1-10; It is characterized in that said load dependence control cock (12), second control cock (37), lifting bellows valve (13) and/or suspension bellow valve (14) have hole or the cooresponding flow cross section that is used for forced air of pipeline that is at least 9mm with diameter.
12. like arbitrary described valve cell (2) among the claim 1-11; It is characterized in that; Second control cock (37) have two mouths (16-1,16-2), wherein; A mouth (16-1) is used to control lifting bellows valve (13), and another mouth (16-2) is used to control suspension bellow valve (14).
13., it is characterized in that second control cock (37) has adjustable switch pressure like arbitrary described valve cell (2) among the claim 1-12.
14., it is characterized in that load-sensing valve (34) is connected with second control cock (37) via throttle structure (35) like arbitrary described valve cell (2) among the claim 1-13.
15., it is characterized in that lifting bellows valve (13) and/or suspension bellow valve (14) are via residual pressure valve (49) and atmosphere like arbitrary described valve cell (2) among the claim 1-14.
16. like arbitrary described valve cell (2) among the claim 1-15; It is characterized in that; Lifting bellows valve (13) and/or suspension bellow valve (14) make up through the combination of 2/2-valve (93) and 3/2-valve (92), and wherein, 2/2-valve (93) and 3/2-valve (92) are controlled through corresponding load dependence control cock (12) respectively; Said load dependence control cock (12) be through electronic control unit (67) according to the load of vehicle by the electromagnetic valve of electric control (68,69).
17., it is characterized in that lifting bellows valve (13) and suspension bellow valve (14) are integrated in the single 5/2-valve (56) or 6/3-valve (74) through at least one load dependence control cock (12) control like arbitrary described valve cell (2) among the claim 1-16.
18., it is characterized in that lifting bellows valve (13) and/or suspension bellow valve (14) are through following operation like arbitrary described valve cell (2) among the claim 1-17
A) electronic control signal, and
B) pneumatic control signal.
19., it is characterized in that lifting bellows valve (13) is through the delivery pressure control of suspension bellow valve (14) like arbitrary described valve cell (2) among the claim 1-18.
20. like arbitrary described valve cell (2) among the claim 1-15; It is characterized in that suspension bellow valve (14) is 4/3-valve (77), said 4/3-valve has two mouth (20-1; 20-2); (5-1 5-2) connects, and said two suspension bellows are associated with the not homonymy of lifting axis for said two mouths and two suspension bellows.
21., it is characterized in that housing (11) comprises the electrical signal ports (66) of the signal of the preceding line direction that is used to represent vehicle or backward direction like arbitrary described valve cell (2) among the claim 1-20.
22. like arbitrary described valve cell (2) among the claim 1-21; It is characterized in that; When detecting or predicting the backward direction, electronic control valve (67) and/or pilot piping control load dependence control cock (12), suspension bellow valve (14) and/or lifting bellows valve (13) and make the state that has by the lifting axis of lifting (3) that is in.
23. among the claim 1-22 arbitrary described valve cell (2) have by the metal suspension spring suspension the axle vehicle in application.
CN201110391935.3A 2010-11-23 2011-11-23 Valve cell Active CN102616105B (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108195574A (en) * 2017-12-27 2018-06-22 浙江工业大学 A kind of control valve valve position concussion experimental method extremely
CN112109512A (en) * 2019-06-20 2020-12-22 动力工程解决方案有限公司 Vehicle suspension system

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11220304B1 (en) 2020-12-22 2022-01-11 Norgren Gt Development Llc Systems and methods for controlling a lift axle

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2652811A1 (en) * 1976-11-20 1978-05-24 Steyr Daimler Puch Ag Retractable trailing axle for lorry - has driven axle load dependent switches to control inflation and deflation of lifting bellows
DE3309729A1 (en) * 1983-03-18 1984-09-27 Bergische Achsenfabrik Fr. Kotz & Söhne, 5276 Wiehl AXLE LIFTING DEVICE
EP0478924A1 (en) * 1990-09-14 1992-04-08 Knorr-Bremse Ag System for controlled raising and lowering of the body of a vehicle equipped with air suspension and height control
JP2973124B2 (en) * 1988-12-03 1999-11-08 ヴアブコ・ヴエステイングハウス・フアールツオイクブレムゼン・ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング Device for obtaining shaft load signal
CN101282863A (en) * 2005-08-22 2008-10-08 阿雷斯工程有限责任公司 Vehicle lifting and/or stabilising device, relative system and process

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060267296A1 (en) 2002-04-23 2006-11-30 Dodd C I Electronic control of vehicle air suspension

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2652811A1 (en) * 1976-11-20 1978-05-24 Steyr Daimler Puch Ag Retractable trailing axle for lorry - has driven axle load dependent switches to control inflation and deflation of lifting bellows
DE3309729A1 (en) * 1983-03-18 1984-09-27 Bergische Achsenfabrik Fr. Kotz & Söhne, 5276 Wiehl AXLE LIFTING DEVICE
JP2973124B2 (en) * 1988-12-03 1999-11-08 ヴアブコ・ヴエステイングハウス・フアールツオイクブレムゼン・ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング Device for obtaining shaft load signal
EP0478924A1 (en) * 1990-09-14 1992-04-08 Knorr-Bremse Ag System for controlled raising and lowering of the body of a vehicle equipped with air suspension and height control
CN101282863A (en) * 2005-08-22 2008-10-08 阿雷斯工程有限责任公司 Vehicle lifting and/or stabilising device, relative system and process

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108195574A (en) * 2017-12-27 2018-06-22 浙江工业大学 A kind of control valve valve position concussion experimental method extremely
CN108195574B (en) * 2017-12-27 2019-12-10 浙江工业大学 control valve position abnormal oscillation experimental method
CN112109512A (en) * 2019-06-20 2020-12-22 动力工程解决方案有限公司 Vehicle suspension system

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KR20120056217A (en) 2012-06-01
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KR101923222B1 (en) 2018-11-28
BRPI1105657A8 (en) 2017-09-12

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