CN102109024A - Electronic control shock absorber - Google Patents
Electronic control shock absorber Download PDFInfo
- Publication number
- CN102109024A CN102109024A CN200910238909XA CN200910238909A CN102109024A CN 102109024 A CN102109024 A CN 102109024A CN 200910238909X A CN200910238909X A CN 200910238909XA CN 200910238909 A CN200910238909 A CN 200910238909A CN 102109024 A CN102109024 A CN 102109024A
- Authority
- CN
- China
- Prior art keywords
- oil storage
- cylinder
- piston
- clutch release
- release slave
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Landscapes
- Vibration Prevention Devices (AREA)
Abstract
The invention relates to an electronic control shock absorber which comprises a working cylinder at the inner layer, an oil storage tank at the intermediate layer, an outer cylinder sleeve at the outer layer, a piston, a piston rod, an upper electromagnetic valve, a lower electromagnetic valve, an upper check valve, a lower check valve, a shock-absorbing spring, an upper cavity and a lower cavity, wherein the piston is arranged in the working cylinder; the piston rod shifts up and down along with the piston; the upper/ lower electromagnetic valve is positioned at the top/ bottom end of the working cylinder to communicate or close the working cylinder and the oil storage tank; the upper/ lower check valve is positioned between the upper/ lower electromagnetic valve and the piston; one end of the shock-absorbing spring is connected with the upper end of the oil storage tank, the other end of the shock-absorbing spring is connected with the upper end of the outer cylinder sleeve; the upper/ lower check valve is communicated with or closes the upper/ lower chamber of the oil storage tank and the working cylinder through opening or closing; the lower end of the outer cylinder sleeve is sealed by an end cover; and the piston rod extends out of the lower electromagnetic valve and is fixedly connected with the end cover to drive the outer cylinder sleeve to shift up and down. The electronic shock absorber provided by the invention has 4 working states (free stretching, only stretch but no contract, only contract but no stretch, no stretch and contract), has a simple structure, has the same overall dimension with the shock absorber, has low cost and reliable performance, the requirement of travelling comfort and control stability for the shock absorber of an automobile can be considered.
Description
Technical field
The present invention relates to vibration damper, more particularly, relate to a kind of automatically controlled vibration damper.
Background technique
Automobile becomes the part in people's life gradually, as means of transportation, people wish that automobile has good riding comfort, to slow down automobile running jolting on uneven road surface, wish also that simultaneously automobile has good control stability, prevent that the body sway of automobile when start to walk acceleration or retarding braking and high speed are curved excessively from rocking, the quality of automobile suspension system is then being taken on the key player who ensures riding comfort and control stability.Automobile suspension system is the elastic structure that connects wheel and vehicle body, and one of its critical piece is a damping shock absorber.Damping shock absorber cooperates with elastic element, plays buffering, vibration damping and maintenance body gesture and acts on stably, and is particularly evident in the unexpected upper and lower motion of automobile or racing, anxious its effect of stopping time.
And need to prove, the riding comfort of automobile and control stability are contradiction to the requirement of automotive suspension: on the one hand, travelling comfort requires suspension soft, and to reduce automobile running jolting on uneven road surface, this just requires the suspension elastic stiffness little with the collocation damping; On the other hand, it is hard that the stability requirement suspension is wanted, with reduce automobile racing, anxious stop and when quickening to start body sway rock, this just require the suspension elastic stiffness and the damping of arranging in pairs or groups big.What general automobile was installed is elasticity and the fixing passive suspension of damping, and the soft or hard of the selection suspension of can only compromising when Automobile Design is to adapt to the fitness for purpose of common operating mode.Obviously, travelling comfort and stability the two all be car steering and take the performance that must guarantee simultaneously in the process, therefore, needs to realize travelling comfort and handling switching rapidly under different situations, also is the little and big switching of rigidity of damper stiffness.
Thus, the passive suspension system of traditional automobile can not satisfy people's requirement, and what arise at the historic moment is semi-active suspension system and active suspension system.This in two suspension system can both regulate automatically according to different pavement behavior and motoring condition, thereby realize travelling comfort and handling switching.But the active suspension system complex structure, power consumption is high, and is on the high side, only has the vehicle of minority costliness to select for use, and most of medium-to-high grade automobiles are then mainly selected semi-active suspension system for use.
Problem is, in present various active or the semi-active suspension, its vibration insulating system still adopts the mode of elastic element collocation damping, promptly change the size of damping or elastic stiffness by electronic control method, can guarantee control stability by strengthening elastic stiffness and damping, also can be by reducing elastic stiffness and damping to obtain riding comfort preferably, but these methods still fail fundamentally to solve vehicle handling stability and the riding comfort situation to automotive suspension requirement contradiction, its system also needs to adopt multiple sensors such as acceleration transducer for the operating mode of distinguishing automobile simultaneously, height sensor, vehicle speed sensor, throttle position switch, braking sensor, steering wheel angle sensor, so that whether judge automobile quickens or retarding braking in starting, the speed of a motor vehicle is high or low, keep straight on and still turn, whether road is smooth etc., so that its electronic control unit decision is increasing or reduces elastic stiffness and damping, the control algorithm more complicated.
Summary of the invention
The technical problem to be solved in the present invention is, can not solve the contradiction and the complex structure problem of riding comfort and control stability at prior art, provide a kind of simple in structure, cost is low, can fundamentally satisfy the automatically controlled vibration damper that riding comfort and control stability require simultaneously.
The technical solution adopted for the present invention to solve the technical problems is: construct a kind of automatically controlled vibration damper, it is characterized in that, the clutch release slave cylinder that comprises internal layer, the oil storage cylinder that surrounds described clutch release slave cylinder in mesosphere, outer field with the outer cylinder sheath of described oil storage cylinder in being enclosed in, be contained in the described clutch release slave cylinder clutch release slave cylinder inside is divided into two not connected on/piston of lower chamber, be contained on the piston with its piston rod that moves up and down, lay respectively at described clutch release slave cylinder top/bottom with by the energising or the outage be communicated with or seal described clutch release slave cylinder and oil storage cylinder on/following solenoid valve, lay respectively at/between following solenoid valve and the piston on/following one-way valve, one end connects the shock-absorbing spring that the described oil storage cylinder upper end the other end connects described outer cylinder sheath upper end, described on/following one-way valve by open or close be communicated with or seal described oil storage cylinder and clutch release slave cylinder on/lower chamber; Described outer cylinder sheath lower end is sealed by end cap, and described piston rod stretches out down solenoid valve and fixedlys connected with described end cap and moves up and down to drive described outer cylinder sheath.
In automatically controlled vibration damper of the present invention, described piston and described clutch release slave cylinder Spielpassung have two circular grooves successively on its cylindrical side, in the radial clearance that is equipped with respectively on the described circular groove between an O RunddichtringO packed-piston and the clutch release slave cylinder inwall.
In automatically controlled vibration damper of the present invention, the upper and lower end face of described piston respectively is equipped with a pad of being convenient to locate, and Upper gasket fixes with self-locking nut and described piston, and the below of lower levelling plate also is equipped with cushion pad.
In automatically controlled vibration damper of the present invention, on described/following one-way valve comprises gasket base, sealing gasket and spring, described gasket base comprises cylindrical portions may and is positioned at the flange circle of cylinder front end, described sealing gasket be enclosed within on the cylindrical portions may and and the flange circle between separated by spring.
In automatically controlled vibration damper of the present invention, on described/following one-way valve also comprises end valve, described end valve is contained in/following one-way valve and corresponding on/following solenoid valve between, and which is provided with the oilhole that is communicated with described clutch release slave cylinder and oil storage cylinder, described oilhole one end is positioned at described oil storage cylinder, and an end is positioned at clutch release slave cylinder and is sealed by described sealing gasket.
In automatically controlled vibration damper of the present invention, on described/following solenoid valve comprises electromagnetic valve body, coil, coil rack, conducting magnetic column, solenoid valve sealing gasket, described solenoid valve sealing gasket covers on the end face of the outside of described electromagnetic valve body, in the described electromagnetic valve body conducting magnetic column is housed, is wound with described coil on the coil rack on the described conducting magnetic column.
In automatically controlled vibration damper of the present invention, between described solenoid valve sealing gasket and the electromagnetic valve body spring is housed, spring will separate between described solenoid valve sealing gasket and the electromagnetic valve body outside end face.
In automatically controlled vibration damper of the present invention, offer the through hole of up/down perforation on the described electromagnetic valve body, and be communicated with described oil storage cylinder on the described through hole, the lower end is communicated with described clutch release slave cylinder.
In automatically controlled vibration damper of the present invention, there is the air chamber that is communicated with described oil storage cylinder described oil storage cylinder upper end, described air chamber is by adapter ring and the two cavity that is sealed of upper end cap, and described adapter ring is assemblied on the circumferential outer surface of described oil storage cylinder upper end, and described upper end cap covers in described adapter ring upper end and by fastening bung flange and adapter ring and is tightly connected.
In automatically controlled vibration damper of the present invention, the lower end of described adapter ring is tightly connected with the upper end of outer T-Ring, the lower end of described outer T-Ring is connected with shock-absorbing spring, the cavity that surrounds between the described adapter ring that is connected successively, outer T-Ring, shock-absorbing spring, outer cylinder sheath, end cap and the oil storage cylinder is a closed cavity, and inside is air.
Implement automatically controlled vibration damper of the present invention, have following beneficial effect: 1) the simple and reliable performance of automatically controlled damper structure of the present invention, the size of whole vibration damper is suitable with existing damping shock absorber size, changes easy accessibility.2) its clutch release slave cylinder, oil storage cylinder, piston etc. all can adopt standard piece, can reduce cost greatly.3) adopt automatically controlled vibration damper of the present invention to substitute traditional damping shock absorber and form suspension, automobile carries the electronic control unit of vibration insulating system and judges the flexible state that determines the control vibration damper according to the signal of body-acceleration sensor and height sensor, the requirement of vehicle ride comfort and control stability can be taken into account, the effectiveness in vibration suppression of the damping shock absorber of damping shock absorber that existing throttle diameter regulates and electric/magnetic rheological damping fluid can be obtained to be better than suspension.
Description of drawings
The invention will be further described below in conjunction with drawings and Examples, in the accompanying drawing:
Fig. 1 is automatically controlled vibration damper first embodiment's of the present invention a structural representation;
Fig. 2 is a piston structure schematic representation embodiment illustrated in fig. 1;
Fig. 3 is an electromagnetic valve structure schematic representation embodiment illustrated in fig. 1;
Fig. 4 is automatically controlled vibration damper second embodiment's of the present invention a structural representation;
Fig. 5 is an electromagnetic valve structure schematic representation embodiment illustrated in fig. 4;
Fig. 6 is a last solenoid valve plan view embodiment illustrated in fig. 4;
Fig. 7 is a C-C sectional view of going up solenoid valve shown in Figure 6.
The corresponding title of label in each accompanying drawing is as follows:
10 clutch release slave cylinders, 20 oil storage cylinders, 21 adapter rings, 22 outer T-Rings, 23 upper end caps, 24 fastening Luo circle, 30 outer cylinder sheaths, one-way valve on 40,50 times one-way valves, 41 gasket bases, 42 sealing gaskets, 43 springs, 44 end valves, 440 oilholes, solenoid valve on 60,70 times solenoid valves, 61 electromagnetic valve bodies, 62 coils, 63 coil racks, 64 conducting magnetic columns, 65 solenoid valve sealing gaskets, 80 pistons, 81O type circle, 82 pads, 83 cushion pads, 90 piston rods, 100 shock-absorbing springs, 200 end caps.
Embodiment
The automatically controlled vibration damper of first embodiment of the invention as shown in Figure 1 comprises clutch release slave cylinder 10, oil storage cylinder 20, outer cylinder sheath 30, last one-way valve 40, following one-way valve 50, goes up solenoid valve 60, following solenoid valve 70, piston 80, piston rod 90, shock-absorbing spring 100 etc.
Wherein, in conjunction with Fig. 1, Fig. 2 as can be known, piston 80 adopts entity structure, does not establish damping hole on it, clutch release slave cylinder 10 is divided into/two parts of lower chamber thereby be contained in the clutch release slave cylinder 10.As shown in Figure 2, piston 80 and clutch release slave cylinder 10 Spielpassung have two O RunddichtringOs 81 to seal on it, guarantee that the clutch release slave cylinder inner carrier is more than 80 and the sealing between following two chambers, that is to say that no liquid flows clutch release slave cylinder 10 upper and lower two chambers by piston 80 is isolated.Piston 80 is upper and lower to be equipped with the pad of being convenient to locate 82, and Upper gasket 82 usefulness self-locking nuts fix, and lower levelling plate 82 belows also are equipped with cushion pad 83.
In conjunction with Fig. 1, Fig. 3 as can be known, the last one-way valve 40 and the following one-way valve 50 that are installed in clutch release slave cylinder 10 tops and bottom are respectively formed by end valve 44, spring 43, sealing gasket 42 and gasket base 41, described gasket base 41 comprises cylindrical portions may and is positioned at the flange circle of cylinder front end, sealing gasket 42 be enclosed within on the cylindrical portions may and and the flange circle between certain distance is arranged, spring 43 is between sealing gasket 42 and flange circle.The end of cylindrical portions may is enclosed within on the end valve 44, and has the oilhole 440 that is communicated with oil storage cylinder 20 and clutch release slave cylinder 10 on the end valve 44, and sealing gasket 42 can cover the end that this oilhole 440 is positioned at 10 li of clutch release slave cylinders.
When the oil pressure of clutch release slave cylinder 10 during more than or equal to the oil pressure of oil storage cylinder 20, thereby spring 43 and clutch release slave cylinder inner fluid pressure withstand on sealing gasket 42 on the end valve 44 oilhole 440 are covered, and clutch release slave cylinder 10 and the oil circuit of oil storage cylinder 20 by oilhole 440 are disconnected; When the oil pressure of oil storage cylinder 20 greater than the oil pressure in the clutch release slave cylinder 10 and when overcoming the thrust of spring 43, the oil of oil storage cylinder 20 enters oilhole 440 and pushes sealing gasket 42 open and enters in the clutch release slave cylinder 10, this means that oil can only one-way flow.
On/following one-way valve 40/50 outer end all is equipped with/following solenoid valve 60/70, in the present embodiment, on/following solenoid valve 60/70 all adopts guide electromagnetic valve, be used for controlling the motion of corresponding/following solenoid valve sealing gasket 65/75 by the control of electric current, thereby the motion of the break-make of control channel 610/710 and end valve sealing gasket 45/75 makes fluid be in connection or off state through the oil circuit that clutch release slave cylinder flows to oil storage cylinder.
In conjunction with Fig. 1, Fig. 3 as can be known, last solenoid valve 60 comprises electromagnetic valve body 61, coil 62, coil rack 63, conducting magnetic column 64, end valve sealing cover 45 and solenoid valve sealing gasket 65, wherein, end valve 44 1 ends are contained on the clutch release slave cylinder end, the other end is connected with electromagnetic valve body and forms chamber, chamber is equipped with end valve sealing gasket 45, and described end valve sealing gasket 45 centres have through hole to be communicated with the sleeve hollow space of gasket base 41 centres of one-way valve, fluid in the clutch release slave cylinder 10 gasket base 41 of can flowing through, then the through hole by end valve sealing gasket 45 flow into end valve sealing gasket 45 with its on conducting magnetic column 64 between clearance channel in.
Because between end valve sealing gasket 45 and the conducting magnetic column on it 64 spring is installed, under the effect of spring, end valve sealing gasket 45 can be pressed on the end valve 44.Spring herein adopts the less spring of the coefficient of stiffiness.When end valve sealing gasket 45 lower surface oil pressure greater than upper surface, then the liquid oil can enter oil storage cylinder 20 through oilhole 440 from end valve sealing gasket 45 lower surfaces in the clutch release slave cylinder 10; When upper surface oil pressure during more than or equal to the lower surface oil pressure, spring and oil liquid pressure are pressed to end valve sealing gasket 45 on the end valve 44, and fluid can not flow to oil storage cylinder via passage 440.Conducting magnetic column 64 is housed in the electromagnetic valve body, is with packing ring skeleton 63 on the circumferential outer surface of conducting magnetic column 64, twining coil 62 on the coil rack 63.As shown in Figure 3, have the through hole 610 of up/down perforation on the electromagnetic valve body 61, and the lower ending opening of through hole 610 is communicated with clearance channel between end valve sealing gasket 45 and the conducting magnetic column 64, and then the oil in the clutch release slave cylinder 10 can flow in the through hole 610 of electromagnetic valve bodies 61 through end valve sealing gasket 45.
Solenoid valve sealing gasket 65 is housed on the upper-end surface of electromagnetic valve body 61, and the center of conducting magnetic column 64 has shrinkage pool to place the spring of Connect Power a magnet valve sealing gasket 65 and a conducting magnetic column 64.Under the effect of spring, during coil 62 no electric circuits, spring will go up solenoid valve sealing gasket 65 jack-up and and keep certain distance between the upper-end surface of electromagnetic valve body 61, make the through hole 610 of electromagnetic valve body 61 be communicated with oil storage cylinder, but oil via through holes 610 in the clutch release slave cylinder 10 and flowing out.There is the air chamber that is communicated with oil storage cylinder 20 tops last solenoid valve 60 upper ends, and this air chamber is upper end cap 23 the two cavity that surround that are assemblied in the adapter ring 21 on the oil storage cylinder 20 top circumference and are tightly connected by fastening bung flange 24 with adapter ring 21 upper ends.When the through hole 610 of electromagnetic valve body 61 does not seal, then directly be communicated with air chamber.For preventing that gas from entering clutch release slave cylinder 10, liquid level must be higher than clutch release slave cylinder 10 tops in the oil storage cylinder 20, so a part of volume of air chamber is equipped with oil.This shows that gas chamber volume must be greater than clutch release slave cylinder 10 volume-variation maximum flows.
When proper functioning, no current in the coil 62 on the conducting magnetic column 64, to reduce heating value, the operating life of solenoid valve 60 in the raising, at this moment, under the effect of spring, solenoid valve sealing gasket 65 flicked and the upper-end surface of electromagnetic valve body 61 between keep certain distance, then the upper end of through hole 610 is not sealed by solenoid valve sealing gasket 65, electromagnetic valve body 61 all communicates with clutch release slave cylinder 10, oil storage cylinder 20, end valve sealing gasket 45 upper and lower surperficial oil pressure are suitable, and liquid oil can be from flowing through outflow with through hole 610 between end valve sealing gasket 45 and the end valve 44.The All Ranges oil pressure equates, but oil free-flow, and this moment, solenoid valve was a channel status.
When coil 62 energising, thereby solenoid valve sealing gasket 65 is drawn onto on the upper-end surface of electromagnetic valve body 61 its through hole 610 sealings, disconnects through the oil circuit of solenoid valve.If pressure are greater than pressure in the oil storage cylinder 20 in the clutch release slave cylinder 10 at this moment, fluid can't flow into, last one-way valve 40 closures, and fluid can't flow to oil storage cylinder 20 through path 440.End valve sealing gasket 45 upper surface pressure are greater than lower surface pressure, end valve sealing gasket 45 is pressed on the end valve 44, gap-closing between the two, fluid also can't flow to oil storage cylinder 20 through this path, and oil pressure is big more in the clutch release slave cylinder 10, and the sealing gasket impacting force is big more, and it is good more to seal, this moment, all paths of clutch release slave cylinder 10 and oil storage cylinder 20 all sealed, and fluid can not flow.If the oil pressure of oil storage cylinder 20 is greater than clutch release slave cylinder 10 oil pressure, fluid can't flow out, and the liquid oil in the oil storage cylinder 20 overcome the spring 43 elastic force acting of going up one-way valve 40, pushes sealing gasket 42 open and enters in the clutch release slave cylinder 10, last one-way valve 40 is a path, and fluid can flow to clutch release slave cylinder through path 440.End valve sealing gasket 45 upper surface pressure are less than lower surface pressure, and fluid can flow to clutch release slave cylinder through end valve sealing gasket 45 and 44 paths of end valve, and then this moment, fluid can flow into, and can not flow out.So after last solenoid valve energising, the path that clutch release slave cylinder epicoele fluid flow to oil storage cylinder disconnects, fluid can't be discharged, and piston can't move upward.
Because the area of through hole 610 much smaller than the area of solenoid valve sealing gasket 65, therefore only needs to use less electromagnetic force can drive 65 work of solenoid valve sealing gasket, working resistance is little, the action sensitivity height, and in allowed band, pressure is big more, and sealing effect is good more.
The same solenoid valve 60 of following solenoid valve 70 working principles because the bottom has piston rod 90 to pass through, so structure be adjusted accordingly, as shown in Figure 1.
Piston rod 90 passes down the respective electrical magnet valve sealing gasket 65 of solenoid valve 70, stretches out down outside the solenoid valve 70, and it is terminal to be fastenedly connected with end cap 200, makes piston rod 90 move up and down can to drive end cap 200 to move simultaneously.At oil storage cylinder 20 outer outer cylinder sheaths 30 in addition, all concyclic heart of oil storage cylinder 20 and clutch release slave cylinder 10 is positioned within the outer cylinder sheath 30 coaxially.The edge of end cap 200 promptly is connected with outer cylinder sheath 30 bottom buckles, makes moving up and down of piston rod 90 be converted into moving up and down of outer cylinder sheath 30.
The top of outer cylinder sheath 30 is to be connected with the end of shock-absorbing spring 100.The shock-absorbing spring 100 of this preferred embodiment is selected pneumatic spring for use.By above known, the adapter ring 21 that forms air chamber is equipped with on the top of oil storage cylinder 20.Adapter ring 21 belows and an outer T-Ring 22 join, and outer T-Ring 22 joins with the top of shock-absorbing spring 100, and then shock-absorbing spring 100, outer cylinder sheath 30, outer T-Ring 22, end cap 200 surround an enclosed cavity jointly with air reservoir 20, have only air in the described cavity.When piston rod 90 drove outer cylinder sheath 30 and moves up and down with wheel, the internal cavities volume of shock-absorbing spring 100 also can change thereupon, produces elastic strain, and cooperating cylinder 10 and oil storage cylinder 20 are reached effectiveness in vibration suppression together.
In the present embodiment, shock-absorbing spring 100 adopts the lower spring of rigidity, to improve damping property, strengthens travelling comfort.Shock-absorbing spring 100 of the present invention also can adopt other various motor springs, as helical spring, leaf spring, torsion bar spring, hydro-pneumatic spring etc.In order to give full play to the superiority of automatically controlled vibration damper, the present invention adopts pneumatic spring and cooperates gas-filled pump, accessory air-space and solenoid electric valve further to improve the overall performance of automotive suspension, as passing through to change the inflation pressure of pneumatic spring, can change vehicle body height easily, can also be by the accessory air-space of solenoid valve shuts pneumatic spring, change the swept volume of pneumatic spring, thereby change the rigidity of pneumatic spring, to be fit to the needs of the different operating modes of automobile.
Oil of the present invention, the damping oil that preferred viscosities is less, it is less to make fluid pass through the damping of solenoid valve, improves sensitivity and travelling comfort.
As shown in Figure 4, in the second embodiment of the present invention, the agent structure of automatically controlled vibration damper and first embodiment are basic identical, comprise equally clutch release slave cylinder 10, oil storage cylinder 20, outer cylinder sheath 30, piston 80, piston rod 90, on/following one-way valve 40/50, on/structure such as following solenoid valve 60/70, air chamber.Wherein the present embodiment and first embodiment's difference is, among first embodiment, on/following solenoid valve 60/70 adopts is guide electromagnetic valve, what present embodiment then adopted is direct action solenoid valve.
The above solenoid valve 60 of direct action solenoid valve is an example, and as Fig. 5, Fig. 6, shown in Figure 7, last solenoid valve 60 comprises electromagnetic valve body 61, coil 62, coil rack 63, conducting magnetic column 64, end valve sealing cover 45 and solenoid valve sealing gasket 65.
Conducting magnetic column 64 is equipped with in sealing gasket 42 upper ends of last one-way valve 40, and in the present embodiment, conducting magnetic column 64 and gasket base 41 are as integrative-structure.Be with coil rack 63 on the circumferential outer surface of conducting magnetic column 64, twining coil 62 on the coil rack 63.Coil 62 is peripherally equipped with columnar electromagnetic valve body 61.Solenoid valve sealing gasket 65 is housed on the upper-end surface of electromagnetic valve body 61, and the center of conducting magnetic column 64 has shrinkage pool to place the spring of Connect Power a magnet valve sealing gasket 65 and a conducting magnetic column 64.Under the effect of spring, the normal condition lower spring with solenoid valve sealing gasket 65 jack-up and and keep certain distance between the upper-end surface of electromagnetic valve body 61, when the solenoid valve energising, then solenoid valve sealing gasket 65 is adsorbed on electromagnetic valve body 61 upper-end surfaces.
As Fig. 6, shown in Figure 7, have the through hole 610 and the oil inlet hole 440 of up/down perforation on the electromagnetic valve body 61, and the upper end of through hole 610 is covered by solenoid valve sealing gasket 65, the lower end does not have sealed pad 42 to cover and is communicated with clutch release slave cylinder 10,440 of oil inlet holes are that the sealed pad 42 in lower end is sealed, and are communicated with oil storage cylinder 20 thereby solenoid valve sealing gasket 65 corresponding positions of upper end have circular hole.In order to guarantee the free flow of liquid oil in solenoid valve, a plurality of through holes 610 and oil inlet hole 440 can be set, guarantee that the flow of liquid oil is enough big, the liquid oil flow damping that makes piston 80 cause when moving up and down is enough little.
The advantage of solenoid valve is simple in structure during straight moving, be swift in response, and processing easily, but owing to directly utilize electromagnetic force shutoff solenoid valve fluid passage, if fluid circulation passage sectional area hour can form damping, and when reducing damping and adopt, then need bigger electromagnetic force during the fluid of the same pressure of shutoff than the major path cross section, coil is had relatively high expectations.Though and first embodiment's guide electromagnetic valve structure relative complex, but can drive with less electromagnetic force/work of following solenoid valve sealing gasket comes the indirect path of shutoff small bore to form high-voltage oil liquid, utilize this high-voltage oil liquid to control the long-pending main fluid passage in shutoff large-section, can control the break-make of big flow fluid like this with less electromagnetic force, electric current in the coil is less, the reliability height, long service life.In actual applications, can select different solenoid valves according to the consideration of aspects such as the demand of the different performances of locomotive and overall cost, resource.
Automatically controlled vibration damper of the present invention usually and automobile real-time state monitoring system be used, its upper and lower solenoid valve 60,70 all links to each other with acceleration transducer in actual applications usually, when acceleration transducer measures vehicle body acceleration is upwards arranged, then make down solenoid valve 70 energisings by certain electric controller; Otherwise,, then go up solenoid valve 60 energisings when measuring downward acceleration.Working state by change solenoid valve like this is with the flow direction of Control work cylinder internal damping oil, thereby the flexible state of control vibration damper reaches the purpose of vibration damping.In concrete the application:
1) when evenness of road surface, when not having height and rising and falling, solenoid valve is in normal working, on/following solenoid valve 60/70 is path, but on the clutch release slave cylinder 10/free-flow of cavity of resorption internal damping oil, the effect that piston 80 does not stress is free state.The weight of vehicle body is born by shock-absorbing spring 100.
2) when bump, wheel make progress accelerated motion, piston 80 moves upward, last solenoid valve 60 outages, following solenoid valve 70 energisings; Then clutch release slave cylinder 10 upper ends are path, but backlash freedom turnover between fluid via through holes 610 and end valve sealing gasket 45 and the end valve 44; Following solenoid valve 60 sealings, following one-way valve 50 one-way passage, fluid can only enter and can not flow out.Because oilhole 440 is much bigger with respect to through hole 610 cross sections, makes liquid oil can flow to outflow swimmingly, then piston 80 can move upward with very little damping.That is to say that the rigidity of whole vibration damper is little, wheel can be rapidly move upward with piston 80 reactions, and vehicle body only is subjected to spring force upwards and very little damping force, thus can keep substantially stable, thereby alleviated the vibration that bump brings.
3) when road surface depression, when wheel quickens to move downward, piston 80 moves downward, last solenoid valve 60 energisings, following solenoid valve 70 cuts off the power supply; Clutch release slave cylinder 10 upper ends are for opening circuit, last one-way valve 40 one-way passage, and fluid can only enter and can not flow out.Following solenoid valve 70 is a path, and fluid can pass in and out by backlash freedom between the through hole 610 of following solenoid valve 70 and end valve sealing gasket 45 and end valve 44.Equally, because liquid oil can free in and out, damping force suffered when piston 80 is moved downward is very little.That is to say that wheel is subjected to spring force and very little damping force, can descend rapidly, thereby slow down the body vibrations that the road surface depression is brought with the support vehicle body.
4) need turn to when vehicle, quicken or during control action such as braking, wheel does not have acceleration, vehicle body is subjected to the inertial force effect, and this moment, upper and lower solenoid valve 60,70 was all switched on, and clutch release slave cylinder 10 upper and lower cavities are and open circuit, one-way valve one-way passage, fluid all can only flow into, and can not flow out.This moment, piston 80 can not move, damper stiffness is big, can not compress or stretch, avoid because the handling that low rigid spring and low viscosity damping oil cause descends, improve the bend passing capacity, the stability of vehicle when guaranteeing acceleration and deceleration, thus guarantee vehicle body height stability constant and vehicle when quickening and slow down.Simultaneously, because through hole 610 areas are little, required electromagnetic force is little, only needs very little Current Control can finish the transformation that vibration damper is little by rigidity, good springiness is big to rigidity, lower wall is steady rapidly, and highly sensitive, energy consumption is low, and reliable performance.
According to above as can be known, the present invention adopts shock-absorbing spring and solenoid valve to come in conjunction with piston motion, and whole vibration damper rigidity is little when needs are realized riding comfort, and damping is very little, and piston can only unidirectionally move, and makes the elastic buffer performance of vibration damper good; When needs were realized control stability, whole vibration damper rigidity was very big, and piston can not move, and vehicle body can be moved rapidly with wheel turn to.
Therefore, automatically controlled vibration damper of the present invention is a kind of controlled flexible vibration damper, 2 unidirectional electrical magnet valves and 2 auxiliary one-way valves to the additional fluid of clutch release slave cylinder are arranged,, can obtain 4 kinds of extreme working staties: 1, freely stretch by connecting and cutting off the electric current that leads to 2 unidirectional electrical magnet valves; 2, only stretch and do not contract; 3, only contract and do not stretch; 4, non-telescoping.
When needing piston to stretch, leave that it moves freely, it then is closed in the other direction it can only unidirectionally be moved; When needing piston motionless, clutch release slave cylinder 10 blocks up and down piston is unable to stir any more.And the damping shock absorber that existing throttle diameter is regulated and the damping shock absorber of electric/magnetic rheological damping fluid, slow down moving of piston though can regulate damping, but control piston moves fully, that is to say, when piston moves up and down, can regulate damping and move it, but still exist piston in the other direction to the possibility that moves; And by increasing damping when making piston keep motionless, still have to have fluid and force the piston upper and lower displacement by damping hole.As seen, automatically controlled vibration damper of the present invention has fundamentally solved the contradiction of riding comfort and control stability, is better than the existing vibration damper of realizing of regulating by damping fully.
In addition, automatically controlled vibration damper of the present invention is simple and reliable, cost is low, and its automatical control system only needs acceleration and two kinds of sensors of vehicle body height just can determine the flexible state of automatically controlled vibration damper, guarantees also can obtain good riding comfort when obtaining good control stability.Piston rod wherein, oil storage cylinder, clutch release slave cylinder, guide sleeve, parts such as oil sealing are equal to general vibration damper, are convenient to large-scale production, reduce cost.Its contour structure size should be suitable with existing damping shock absorber, so also simplified the design and convenient installation of system.
In conjunction with the accompanying drawings embodiments of the invention are described above; but the present invention is not limited to above-mentioned embodiment; above-mentioned embodiment only is schematic; rather than it is restrictive; those of ordinary skill in the art is under enlightenment of the present invention; not breaking away under the scope situation that aim of the present invention and claim protect, also can make a lot of forms, these all belong within the protection of the present invention.
Claims (10)
1. automatically controlled vibration damper, it is characterized in that, the clutch release slave cylinder (10) that comprises internal layer, the oil storage cylinder that surrounds described clutch release slave cylinder (10) (20) in mesosphere, outer field with the outer cylinder sheath (30) of described oil storage cylinder (20) in being enclosed in, be contained in the described clutch release slave cylinder (10) clutch release slave cylinder (10) inside is divided into two not connected on/piston (80) of lower chamber, being contained in piston (80) goes up with its piston rod that moves up and down (90), lay respectively at described clutch release slave cylinder (10) top/bottom be communicated with by energising or outage or seal oil circuit between described clutch release slave cylinder (10) and the oil storage cylinder (20) on/following solenoid valve (60/70), lay respectively at/between following solenoid valve (60/70) and the piston (80) on/following one-way valve (40/50), one end connects the shock-absorbing spring (100) that described oil storage cylinder (20) the upper end the other end connects described outer cylinder sheath (30) upper end
On described/following one-way valve (40/50) by open or close be communicated with or seal described oil storage cylinder (20) and clutch release slave cylinder (10) on/oil circuit between the lower chamber;
Described outer cylinder sheath (30) lower end is by end cap (200) sealing, and described piston rod (90) stretches out down solenoid valve (70) and fixedlys connected with described end cap (200) and moves up and down to drive described outer cylinder sheath (30).
2. automatically controlled vibration damper according to claim 1, it is characterized in that, described piston (80) and described clutch release slave cylinder (10) Spielpassung, have two circular grooves on its cylindrical side successively, in the radial clearance that is equipped with respectively on the described circular groove between an O RunddichtringO (81) packed-piston (80) and clutch release slave cylinder (10) inwall.
3. automatically controlled vibration damper according to claim 2, it is characterized in that, the upper and lower end face of described piston (80) respectively is equipped with a pad of being convenient to locate (82), and top pad (82) is fixing with self-locking nut and described piston (82), and the below of following pad (82) also is equipped with cushion pad (83).
4. automatically controlled vibration damper according to claim 1, it is characterized in that, on described/following one-way valve (40/50) comprises gasket base (41), sealing gasket (42) and spring (43), described gasket base (41) comprises cylindrical portions may and is positioned at the flange circle of cylinder front end, described sealing gasket (42) be enclosed within on the cylindrical portions may and and the flange circle between separated by spring (43).
5. automatically controlled vibration damper according to claim 4, it is characterized in that, on described/following one-way valve (40/50) also comprises end valve (44), described end valve (44) is contained in/following one-way valve (40/50) and corresponding on/following solenoid valve (60/70) between, and which is provided with the oilhole (440) that is communicated with described clutch release slave cylinder (10) and oil storage cylinder (20), described oilhole (440) one ends are positioned at described oil storage cylinder (20), and the other end is positioned at clutch release slave cylinder (10) and is sealed by described sealing gasket (42).
6. automatically controlled vibration damper according to claim 1, it is characterized in that, on described/following solenoid valve (60/70) comprises electromagnetic valve body (61), coil (62), coil rack (63), conducting magnetic column (64) and solenoid valve sealing gasket (65), described solenoid valve sealing gasket (65) covers on the outside end face of described electromagnetic valve body (61), conducting magnetic column (64) is housed in the described electromagnetic valve body (61), is wound with described coil (62) on the coil rack (63) on the described conducting magnetic column (64).
7. automatically controlled vibration damper according to claim 6 is characterized in that, between described solenoid valve sealing gasket (65) and the electromagnetic valve body (61) spring is housed, and spring will separate between described solenoid valve sealing gasket (65) and electromagnetic valve body (61) outside end face.
8. automatically controlled vibration damper according to claim 7 is characterized in that, offers the through hole (610) of up/down perforation on the described electromagnetic valve body (61), and is communicated with described oil storage cylinder (20) on the described through hole (610), and the lower end is communicated with described clutch release slave cylinder (10).
9. automatically controlled vibration damper according to claim 8, it is characterized in that, there is the air chamber that is communicated with described oil storage cylinder (20) described oil storage cylinder (20) upper end, described air chamber is by adapter ring (21) and upper end cap (23) cavity that the two sealed, and described adapter ring (21) is assemblied on the circumferential outer surface of described oil storage cylinder (20) upper end, and described upper end cap (23) covers in described adapter ring (21) upper end and by fastening Luo circle (24) and adapter ring (21) and is tightly connected.
10. automatically controlled vibration damper according to claim 9, it is characterized in that, the lower end of described adapter ring (21) is tightly connected with the upper end of outer T-Ring (22), the lower end of described outer T-Ring (22) is connected with shock-absorbing spring (100), the cavity that surrounds between the described adapter ring (21) that is connected successively, outer T-Ring (22), shock-absorbing spring (100), outer cylinder sheath (30), end cap (200) and the oil storage cylinder (20) is a closed cavity, and inside is air.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910238909XA CN102109024B (en) | 2009-12-29 | 2009-12-29 | Electronic control shock absorber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910238909XA CN102109024B (en) | 2009-12-29 | 2009-12-29 | Electronic control shock absorber |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102109024A true CN102109024A (en) | 2011-06-29 |
| CN102109024B CN102109024B (en) | 2012-08-22 |
Family
ID=44173271
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910238909XA Expired - Fee Related CN102109024B (en) | 2009-12-29 | 2009-12-29 | Electronic control shock absorber |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102109024B (en) |
Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102364154A (en) * | 2011-10-25 | 2012-02-29 | 杭州星迈新材料技术有限公司 | Passive damping adjustable magneto-rheological fluid shock absorber |
| CN103244495A (en) * | 2013-04-26 | 2013-08-14 | 武汉理工大学 | Electrical control rectifying valve of hydraulic electric feed energy shock absorber |
| CN103711829A (en) * | 2014-01-06 | 2014-04-09 | 浙江中兴减震器制造有限公司 | Tri-cylinder self-adaption type anti-falling shock absorber |
| CN105090337A (en) * | 2014-11-20 | 2015-11-25 | 芜湖蓝宙电子科技有限公司 | Controllable telescopic shock absorber |
| CN106678254A (en) * | 2016-12-21 | 2017-05-17 | 中国矿业大学 | Magneto-rheological absorber and working method thereof |
| US9695900B2 (en) | 2009-10-06 | 2017-07-04 | Tenneco Automotive Operating Company Inc. | Damper with digital valve |
| CN107035804A (en) * | 2017-06-08 | 2017-08-11 | 新疆沙漠虎特种车辆科技有限公司 | A kind of damper of vehicle |
| US9802456B2 (en) | 2013-02-28 | 2017-10-31 | Tenneco Automotive Operating Company Inc. | Damper with integrated electronics |
| US9879746B2 (en) | 2013-03-15 | 2018-01-30 | Tenneco Automotive Operating Company Inc. | Rod guide system and method with multiple solenoid valve cartridges and multiple pressure regulated valve assemblies |
| US9879748B2 (en) | 2013-03-15 | 2018-01-30 | Tenneco Automotive Operating Company Inc. | Two position valve with face seal and pressure relief port |
| US9884533B2 (en) | 2013-02-28 | 2018-02-06 | Tenneco Automotive Operating Company Inc. | Autonomous control damper |
| US9925842B2 (en) | 2013-02-28 | 2018-03-27 | Tenneco Automotive Operating Company Inc. | Valve switching controls for adjustable damper |
| CN108458026A (en) * | 2018-05-22 | 2018-08-28 | 杨华富 | A kind of gas spring and door |
| US10479160B2 (en) | 2017-06-06 | 2019-11-19 | Tenneco Automotive Operating Company Inc. | Damper with printed circuit board carrier |
| US10588233B2 (en) | 2017-06-06 | 2020-03-10 | Tenneco Automotive Operating Company Inc. | Damper with printed circuit board carrier |
| CN112576680A (en) * | 2019-09-30 | 2021-03-30 | 比亚迪股份有限公司 | Shock absorber and vehicle |
| CN115875394A (en) * | 2022-11-10 | 2023-03-31 | 上海保隆汽车科技(安徽)有限公司 | Shock absorber visor and shock absorber assembly |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1557059A (en) * | 1967-11-29 | 1969-02-14 | ||
| DE69415778T2 (en) * | 1993-11-13 | 1999-05-20 | Delphi France Automotive Systems Immeuble Vision Defense, La Garenne-Colombes | Shock absorber |
| DE4424436C2 (en) * | 1994-07-12 | 1997-11-27 | Mannesmann Sachs Ag | Shut-off valve assembly for a vibration damper |
| CN1560491A (en) * | 2004-02-19 | 2005-01-05 | 川 郭 | Electrici controlled type variable damping attenuator |
-
2009
- 2009-12-29 CN CN200910238909XA patent/CN102109024B/en not_active Expired - Fee Related
Cited By (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9695900B2 (en) | 2009-10-06 | 2017-07-04 | Tenneco Automotive Operating Company Inc. | Damper with digital valve |
| US9810282B2 (en) | 2009-10-06 | 2017-11-07 | Tenneco Automotive Operating Company Inc. | Damper with digital valve |
| CN102364154B (en) * | 2011-10-25 | 2013-03-13 | 杭州星迈新材料技术有限公司 | Passive damping adjustable magneto-rheological fluid shock absorber |
| CN102364154A (en) * | 2011-10-25 | 2012-02-29 | 杭州星迈新材料技术有限公司 | Passive damping adjustable magneto-rheological fluid shock absorber |
| US10000104B2 (en) | 2013-02-28 | 2018-06-19 | Tenneco Automotive Operating Company Inc. | Damper with integrated electronics |
| US9884533B2 (en) | 2013-02-28 | 2018-02-06 | Tenneco Automotive Operating Company Inc. | Autonomous control damper |
| US9925842B2 (en) | 2013-02-28 | 2018-03-27 | Tenneco Automotive Operating Company Inc. | Valve switching controls for adjustable damper |
| US9802456B2 (en) | 2013-02-28 | 2017-10-31 | Tenneco Automotive Operating Company Inc. | Damper with integrated electronics |
| US9879746B2 (en) | 2013-03-15 | 2018-01-30 | Tenneco Automotive Operating Company Inc. | Rod guide system and method with multiple solenoid valve cartridges and multiple pressure regulated valve assemblies |
| US9879748B2 (en) | 2013-03-15 | 2018-01-30 | Tenneco Automotive Operating Company Inc. | Two position valve with face seal and pressure relief port |
| CN103244495A (en) * | 2013-04-26 | 2013-08-14 | 武汉理工大学 | Electrical control rectifying valve of hydraulic electric feed energy shock absorber |
| CN103711829A (en) * | 2014-01-06 | 2014-04-09 | 浙江中兴减震器制造有限公司 | Tri-cylinder self-adaption type anti-falling shock absorber |
| CN103711829B (en) * | 2014-01-06 | 2016-01-20 | 浙江中兴减震器制造有限公司 | Three self-adapting type anti-dumping vibration dampers |
| CN105090337A (en) * | 2014-11-20 | 2015-11-25 | 芜湖蓝宙电子科技有限公司 | Controllable telescopic shock absorber |
| CN106678254A (en) * | 2016-12-21 | 2017-05-17 | 中国矿业大学 | Magneto-rheological absorber and working method thereof |
| US10479160B2 (en) | 2017-06-06 | 2019-11-19 | Tenneco Automotive Operating Company Inc. | Damper with printed circuit board carrier |
| US10588233B2 (en) | 2017-06-06 | 2020-03-10 | Tenneco Automotive Operating Company Inc. | Damper with printed circuit board carrier |
| CN107035804A (en) * | 2017-06-08 | 2017-08-11 | 新疆沙漠虎特种车辆科技有限公司 | A kind of damper of vehicle |
| CN107035804B (en) * | 2017-06-08 | 2023-08-04 | 高碑店市龙程汽车制造有限公司 | Vehicle damping device |
| CN108458026A (en) * | 2018-05-22 | 2018-08-28 | 杨华富 | A kind of gas spring and door |
| CN112576680A (en) * | 2019-09-30 | 2021-03-30 | 比亚迪股份有限公司 | Shock absorber and vehicle |
| CN115875394A (en) * | 2022-11-10 | 2023-03-31 | 上海保隆汽车科技(安徽)有限公司 | Shock absorber visor and shock absorber assembly |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102109024B (en) | 2012-08-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102109024B (en) | Electronic control shock absorber | |
| CN201575099U (en) | Controllable extension and retract shock absorber | |
| CN201575100U (en) | Controllable extension and retract shock absorber | |
| CN2811665Y (en) | Single-chamber oil-gas separation type oil-gas spring with nonlinear characteristics | |
| CN204083040U (en) | For the miniature noise elimination accumulator of vibration damper | |
| CN202790297U (en) | Temperature-controllable magnetorheological fluid bumper | |
| CN101349316B (en) | Sensing load damp-changing or controllable sensing load damp-changing shock mitigation system | |
| CN103802626A (en) | Vehicle suspension system | |
| CN106523574B (en) | A kind of multi-state damping adaptive hydro-pneumatic spring and its control method | |
| CN103527697A (en) | Hydro-pneumatic spring suspension cylinder | |
| CN105889390A (en) | Novel vibration damping supporting column | |
| CN104709025A (en) | Self-road-adaption hydraulic active suspension system | |
| CN100441901C (en) | Variable damping shock absorber | |
| CN101725658A (en) | Dead load, dynamic pulse and stretching speed self-adaptive resistance variation method and damper | |
| CN205896020U (en) | Half initiative pneumatic suspension unit of high speed train with adjustable rigidity and damping | |
| CN104154168B (en) | A kind of miniature noise elimination accumulator for damper | |
| CN106090104A (en) | Controllable extensible vibroshock | |
| CN104948644A (en) | Controllable telescopic damper | |
| CN106151357B (en) | A kind of rigidity and the active air suspension arrangement of damp adjustable bullet train half | |
| CN109114158B (en) | Combined vibration damper for car | |
| CN105090337A (en) | Controllable telescopic shock absorber | |
| CN205503852U (en) | Binocular hydraulic damper with mend oil in time, fully | |
| US11242906B2 (en) | Variable damping force shock absorber | |
| CN107654558A (en) | A kind of vehicle shock absorber | |
| CN203348403U (en) | Front vibration damper assembly of compound automobile |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20120822 Termination date: 20211229 |