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    • 专利摘要:

    公开号:SE0900543A1
    申请号:SE0900543
    申请日:2009-04-23
    公开日:2010-10-24
    发明作者:Lars Soensteroed；Haakan Malmborg；Benny Ewers
    申请人:Oehlins Racing Ab；
    IPC主号:
    专利说明:

    10152025302determined by the regulator area. This means that the opening takes place abruptly at onecertain pressure difference across the washer determined by the regulating force Fr and dethe restraining forces, which may, for example, be a restraining forcesum force Fa created by some or all of spring forces Fs, pilot forces Fpand additional flow and frictional forces Fq.
    The applicant has in previously designed pressure regulators, published in patentsEP0942195 and schematically described in Figure 2, solved the problem with itabrupt the pressure increase by introducing two serial, stroke-type,first and second throttles with a first d1 "and a second diameter d2"and a fixed third throttle arranged in parallel with the first throttlewith a certain third diameter d3 ”. The locations of these throttles providecontroller areas Ar1 ", Ar2" on which two different controller pressures P1 ", P2" act.
    The first regulator area Ar1 "on which the main pressure P1" acts isdetermined by the diameter d1 "and the second regulating area Ar2" on which oneintermediate pressure P2 "seems to be determined by the difference between the diameters d2" andd1 ”. The product of the respective regulator area and regulator pressure becomes itopening the regulating force Fr.
    The flow resistance RS1 ", RS2" through the first and the secondthe throttle is determined by the respective throttle curtain area As1 ", As2"times a flow coefficient Kq ”. The first and the second curtaineansAs1 ", As2" size is thus determined by the diameters of the choke d1 ", d2"times the valve strokes s and pi. Because the third choke is fixed andnot dependent on the stroke, the flow through the third throttle is determined onlyof its area Af "which is determined the third diameter d3" according to the formulaAf "= pi / 4 * d3" 2. The parallel connection of the first and the third chokeprovides that the flow resistance for each choke can be added and canis called a first flow resistor RS1 "+ Rf". Series couplingsbetween the second choke with a second flow resistor Rs2 ”andthe parallel-connected throttles with the first flow resistor10152025303RS1 "+ Rf" causes a multiplication of the resistors. Thus, the totalthe throttling resistance is described as:R "= (Rs1" + Rf ") * Rs2" / ((Rs1 "+ Rf") 2 + Rs2 "2) ° -5The parallel connection of the first and the third chokecurtain areas / areas As1 "and Af" thus means that the flow resistancein the case of the two parallel chokes, RS1 becomes "+ Rf". Same flow q "flows through these parallel-connected throttles as through itthe second choke As2 ”. This means that the pressure drop due to the firstthe flow resistance Rs1 "+ Rf" is p1 "- p2" and the pressure drop due to thethe second flow resistor Rs2 "is p2".
    For small flows / strokes - that is, when the stroke s is zero or near zero - is p1 ”equal to p2 ”and with increasing flows / strokes the pressure decreases p2” in relation top1 ”. The decrease occurs because the flow resistance Rs1 "+ Rf" becomes moredominant compared to Fls2 ”in its dependencies of the kind p. This implies thatthe valve both opens and closes with a gentle movement where the opening andthe closing effect keeps the pressure down at the beginning of the stroke and then givesincreasing pressure.
    However, this soft-opening solution has disadvantages such as that the geometry isdifficult to vary, it is tolerance sensitive and works above all just forflow direction from inside and out it wants to saw excludes a double-actingfeature.This patent application thus describes a shock absorber valve / pressure regulatorwith soft opening according to a new construction that does not have these disadvantagesand which can also be used in a variety of applications.1015202530Object of the inventionThe present invention relates to a pressure regulator intended for use in ashock absorber valve. The pressure regulator should open with a gentle movement at the same timeas it should be easy to adapt to different applications.
    The invention also intends to create a pressure regulator with a robustconstruction which is relatively insensitive to tolerances but which also providesgreater constructive freedom, for example in cases where a double-acting functionsought.
    Furthermore, the invention aims to create a pressure regulator which is simple andcheap to both manufacture, assemble and adjust.
    Summary of the inventionThe pressure regulator according to the invention is intended to adjust the pressure of atotal damping fluid flow in a shock absorber valve between an upstream anddownstream volume where a first and a third pressure prevail.
    The pressure regulator comprises a first adjusting part which moves axially with a stroke inrelative to a seat portion having a first side comprising at least a firstand a second seat. When the adjusting part moves with an axial stroke in relation tothe seat part creates a flow opening varying with the stroke between the partswhich are arranged to restrict the total damping medium flow between itTheCharacteristic of the invention is that the seat part comprises at least twoupstream and downstream volume. which isparallel first and second throttles whose flow restricting abilitydetermined by the design of the seats. The seat part also includes one with itthe second choke serially arranged fixed third choke. The first andthe second throttle varies with the stroke so that it through the firstthe throttle passes a first damping medium flow and through the second and thethird throttling goes a second damping media flow where the relationship betweenthe first and second damping media flows increase with increasing stroke.10152025305What distinguishes this soft-opening solution from prior art is thatthe different throttles are arranged in a different sequence, which means advantages inform of a virtually unrestricted freedom as to the geometry of itsought the soft opening. The new geometry can handle everyoneflow directions and can thus also be made double-acting.In a first embodiment of the pressure regulator are the first and the secondthe throttle defined by a first and a second seat diameter. Thisseat diameter is equivalent to the respective circumference of the throttles, that issay the throttles do not have to be circular but can have in principle whichgeometric shape at any time.
    The first and second throttling can be described as varying with the strokeby their curtain areas depending on the choke diameter and strokeincreases and lets through a larger flow of damping medium as the stroke increases.
    At the same time, the third fixed serially arranged throttle ensures that the secondthe damping media flow is restricted more than the first damping media flow because itthe second damping medium flow is forced by two throttles.In a second embodiment of the invention, the first side of the seat part hascut-outs arranged within the circumference of the first and second seats.
    These cutouts create first and second volumes arranged inthe seat part. The attenuation medium that is in the volumes gets dueflow a certain pressure determined by the size of the throttles.
    The third choke may be formed as a hole with a thirddiameter which is arranged in the seat part. The hole then creates a flow openingbetween the upstream volume and the other volume. Thethe third choke can also be designed as a groove with a width anda depth extending between the first and second volumes. l boththese embodiments of the third choke, it is arranged in series10152025306with the second throttling, which means the second damping medium flowthrottles more than the first damping fluid flow.
    The first and second volumes can also be said to be arranged asa first throttling unit which is repeated at least once on the seat partfirst page. If at least two throttling units are arranged on the seat partfirst side, these can be symmetrically placed on the seat part. The flowbetween the damping chambers then creates an even pressure on the adjusting part of the liftcontrolled and mainly parallel to the seat part.
    The throttling units can also be placed asymmetrically on the seat partwhen a certain angle of the adjusting part is desired when it lifts from the seat part. With aangle of the adjusting part, the pressure in the damping medium flow can be further adjusted.In a fifth embodiment, the seat part also has a second side, opposite itfirst page, one or more other throttling units arranged. Thus hasthe seat part throttling units both on it towards and from the direction of movementknowing side. The design of the seat part means that damping medium can flowboth equalpressure adjustment, that is, have a soft-opening character in boththrough the seat part in the directions of mainlyflow directions.In a further embodiment, the pressure regulator is intended to adjust ittotal damping medium flow between a first and a second damping chamberseparated by a delimiting part. The delimiting part can be a piston, armor the like which moves with a design determined by the surroundingsspeed in a damping unit such as a shock absorber, front fork orsteering dampers. The damping medium is then arranged to be able to flow throughthe pressure regulator via the first throttling units in a direction from itfirst to the second damping chamber and also in a direction from the secondto the first damping chamber through the second throttling units.
    The pressure regulator can be located in an external unit outside the damping bodyor it is arranged mounted directly in the delimiting part of the shock absorber.1015202530The invention is described in more detail below, with reference toaccompanying drawings.
    List of figuresFig. 1 shows a first known variant of a simple pressure regulatorFig. 2 shows a second known variant of a soft-opening pressure regulatorFig. 3a shows a schematic view of the flow through the inventionthe pressure regulator.
    Fig. 3b shows the pressure regulator according to the invention in cross section at threedifferent sizes of actuator strokesFig. 3c shows an alternative embodiment of the third chokeFig. 4 shows the first embodiment of the invention as a pressure regulator inform of a non-return valveFig. 5 shows an example of a pilot-controlled valve with the invention according to the inventionthe pressure regulatorFigs. 6a-d show alternative embodiments of the seat partFigure 7 shows a double-acting pilot-controlled shock absorber valve with apressure regulator where flows are allowed in both the compression and return directionFigs. 8a-b show a side view of a part of the piston unit with the parts that areactive during a compression and a return stroke, respectively.
    Fig. 9 shows a pilot-controlled shock absorber valve including itthe pressure regulator according to the invention.
    Figs. 10a and 10b show a schematic view of a shock absorber with apilot-controlled shock absorber / entil and how the damping medium flows during a returnrespectively a compression strokeDetailed description of the inventionFigure 3a shows a schematic view of the flow through the inventionthe pressure regulator. The pressure regulator 1 is located in a flow path q between oneshock absorbers, of a delimiting part HP delimited damping chamber DC1,DC2. The application is not limited to shock absorbers that perform one10152025308telescopic movement but may also include, for example, rotary dampers.
    The flow q between the damping chambers DC1, DC2 can take place either throughthe delimiting part HP or through channels arranged outside the respectivedamping chamber.
    When the shock absorber piston moves at a speed v, the pressure regulator opensand a damping medium flow q can flow in a first flow q1 over a firstthrottle 4a with a first impact-dependent curtain area As1 and in a secondflow q2 over a second and a third throttle 5a, 6a with a stroke dependent incurtain area As2 and a fixed area Af that does not cooperate with the battle.
    The definitions of curtain area can be seen in figure 3b. A first press p1 actsupstream of the throttles in the upstream volume V., and athird pressure p3 acts in it downstream of the throttles arrangedvolumes Vd. It appears between the third 6a and the second throttle 5asecond pressure p2. The first and second throttles 4a, 5a are parallelwith each other and with one stroke variable. The third choke 6a isfixed, ie not dependent on the type, and serially arranged with the otherthe choke 5. The first and the second choke 4a, 5a vary withthe blow because their curtain areas As1, As2 increase with increasing blow. Butsince the third fixed choke 6a is connected in series with the secondthe throttle throttles the second flow q2 of damping medium more than the firstthe flow q1 so that the ratio of the first to the secondthe damping medium flow q1 / q2 increases with increasing stroke s. Thus, the other decreasesthe pressure p2 in relation to the first pressure p1 between the third 6a and thethe second throttle 5a more than the pressure drop provided by the base flow qover the first throttle 4a, i.e. the difference between the third and thefirst pressure p3-p1. For small strokes, the damping medium flow is so low that the firstthe pressure P1 and the second pressure P2 are almost equal.
    Figure 3b shows the pressure regulator according to the invention in cross section atthree different sizes of the stroke of the adjusting part in relation to the seat part - forFor the sake of clarity, only half the controller is displayed. The pressure regulator comprises a10152025309movable adjusting part 3 which works against a seat part 2 including at least onefirst and a second seat 4, 5. The adjusting plate 3 is in this case a circular washer.
    This adjusting part 3 divides the pressure regulator into at least one upstream Vu and onedownstream volume Vu. The seat part 2 has cut-outs arranged inside itthe circumference of the first 4 and the second seat 5. These cutouts form firstand other volumes V1, V2. In the upstream and downstream, respectivelyarranged volume Vu, Vu, the above-mentioned upstream anddownstream arranged pressures p1, p3. These pressures are caused by a pressure dropwhich is dependent on the pressure-affected regulator areas Ar1, Ar2 of the actuator part 3Thethe control areas Ar1, Ar2 have a circumference of 0.1, 05 which is defined by the seatsand its respective opening degree / stroke p. pressure affectedplacement in the seat part. About the pressure-affected regulators Ar1, Ar2circumference 0.1, 05 is multiplied by the distance / stroke s which the valve openscreates a column with a defined curtain area As1, As2 through which it ispossible for the damping medium to flow.
    When the adjusting part 3 opens, it is moved a distance from its rest position towards itthe first and second seats 4, 5 described by the stroke s. The stroke s is a function of3, as thenthe pressure regulator is open can flow with the first flow q1 between itdamping medium flow q, created by the pressure drop across the adjusting partthe first seat 4 and the adjusting part 3 and with the second flow q2 between the secondthe seat 5 and the adjusting part 3. The first volume V1 is mainly directconnected to the upstream volume Vu while the other volumeV2 is connected to the upstream volume Vu via the fixedthe throttle 6a. Due to the direct connection of the first volume V1 tothe upstream volume Vu is the pressure also in the first volume V1substantially equal to the first pressure p1. Through interconnectionbetween the second volume V2 and the volume Vu via the fixed choke 6ais, at small strokes s and flows q, also the second pressure p2 mainlyequal to the first pressure p1.101520253010The soft opening according to the invention is thus created by at least onethrottling unit RU comprising two parallel, stroke-variable,first and second throttles 4a, 5a which can be said to have one with the circumference04, 05 equivalent first d1 and second diameter d2 and one with the otherthe throttle serially arranged fixed third throttle 6a with a thirdequivalent diameter d3. The first and second throttles varybattle because their curtain areas As1, As2, which depend on the firstand the design of the second volume V1, V2, increases. This means that theylets through a larger flow of damping medium with the blow s. Butsince the third fixed choke 6a interconnects the secondvolume V2 and the upstream volume V1, the second is throttledthe flow q2 of attenuation medium more to the second volume V2 than the first flowq1 to the first volume V1. Thus, the pressure p2 in the other dropsthe volume V2 in relation to the pressure p1 in the first volume V1 then the adjusting parthas moved more than a certain small stroke. At small strokes, roughly equal to zero, isthe vapor medium flow so low that the pressure in both the first and the secondthe volume V1, V2 is almost equal to the first pressure p1.
    The first pressure p1 acting on the regulator area Ar1 creates a firstregulator force Fr1 and the second pressure p2 acted on the regulator areaAr2 creates a second regulating force Fr2. Both forces act in openingdirection of the adjusting part 2, thus they can be added to form a totalregulator power Fr. This total regulating force Fr can be balanced by oneabutting sum force Fa created by any or all of the spring forces Fs,pilot forces Fp and additional flow and frictional forces Fq, see alsothe following embodiments of the invention and mathematical descriptionbelow. Since the pressure p2 decreases in relation to the main pressure p1 witha rate of decrease determined by the size of the thirdthe throttle 6a also reduces the second regulating force Fr2 in proportionto the first regulating force Fr1. Since the first pressure p1 acts inprinciple without series throttling directly on the first controller area Ar1 comesthe first regulating force Fr1 thus to increase in proportion to the decrease of101520253011the second regulating force Fr2 whereby the main pressure p1 increases with the totalthe flow q.
    Thus, the main pressure p1 in the first volume V1 is dominant and controllingat larger strokes and a variation of the pressures p1, p2 in the two volumesV1, V2 preferably take place continuously in proportion to the stroke s. With helpof well-tuned size of the fixed throttle 6a in combination withthe size of the first and second throttles 4a, 5a can be soft openingachieved. This can be described mathematically as below.
    The flow resistor RS1, RS2, Rf through the different throttlesdetermined by the respective throttling curtain area As1, As2 and the fixed onethrottle area Of times a flow coefficient Kq. Gardinareornas As1, As2size is determined by the equivalent diameters dl, d2 times pi of the throttlesand valve stroke s.
    The series connection of Af and As2 means that the flow resistance ofthese two strangulations together can be expressed:R2 = Rs2 * Rf / (Rs22 + | =: f2) ° -5For the entire throttling unit RU, q = q1 + q2, which means that ifthe flow resistance of the whole circuit is expressed by R is obtained fromregulated head pressure p1 connection:R * p1 ° * 5 = Rs1 * p1 ° '5 + R2 * p1 °' 5The fact that the two resistors H2 and Fist are connected in parallel thus givesR = R2 + Rs1The FlU flow resistance of the entire throttling unit thus becomesR = Rs2 * Rf / (Rs22 + Rf2) ° ~ 5- »Rs1To further develop the reasoning, the force balance on the actuator part can also3 is described mathematically according to the following formulas:101520253012For the total regulating force Fr, the following applies:Fr1 = Ar1 * p1where Ar1 = Pi / 4 * d12 and p1 is the regulated main pressure acting in itfirst volume V1Fr2 = Ar2 * p2Where Ar2 = Pi / 4 * d22 and p2 is the pressure acting in the second volume V2The pressure p2 in the second volume V2 is obtained via the flow connections:q2 = Rf * (p1-p2) ° -5 = Rs2 * p2 ° -5from which an expression for p2 can be solved as a function of p1pz = p1 * (nfz / rnszz + nf2))The total regulating force Fr can thus be expressed as thatthe main pressure p1 acts on an imaginary regulatory ar that can be released fromthe formula:p1 * Ar = p2 * Ar2 + p1 * Ar1 = p1 * (Rf2 / (Rs22 + Rf2)) * Ar2 + p1 * Ar1and thus expressed:Ar = (nf2 / (Rs22 + Rf2)) * Ar2 + Ar1The force equilibrium on the frame part 3 can also be expressed mathematically bythe following relationship which describes the pilot thrust which acts inopposite direction for the opening of the actuator part 3:Fp = Pp * ApWhere Ap is the area that creates the force on the frame part 3 in the closing directionand which is preferably the area of those described in connection with Figure 7plungen / arna 13a, 13b. The pressure which acts via the plungers 13a, 13bthe actuating part 3 is a pilot pressure Pp, also this is described in more detail in connectionwith Figures 7 and 9.101520253013According to Figure 7, a main spring also acts on the plunger (s) 13a, 13b14a, 14b which has a main spring constant is C and a bias voltage is spwherein the spring force Fs varying with the stroke s can be expressed:Fs = C * (s + sp)The flow forces Fq acting on the actuating part 3 can be simply expressedas:Fq = Kfq * Kq * Ka * s * p1 = Kfq * R * p1Where the product of flow coefficient Kq, area coefficient Ka and the kind sinterpreted as a stroke-dependent throttling R = Kq * Ka * s. The coefficient of flowKfq has been taken from Bernulli's generally known hydropower equationFqzKfqwfqlkpOßlThe regulating force Fr, intended as the product of Ar * p1, is balanced by the sumof the sub-forces arising from springs Fs, flow forces Fq and iwhere applicable pilot pressure forces Fp. That is: iFr = Fp + Fs + FqWhich brings us to the final formula:Ar * p1 = C * (s + sp) + Kfq * R * p1 + Pp * ApWhere p1 can be triggered and expressed explicitly as a result of the force balance.p1 = ZFa / ZAr = (pp * Ap + C * (s + sp)) / (Ar-Kfq * R)It then becomes obvious according to the simplified flow theory thatthe adjusting forces Fa must be distinguished and that part of the flow forcesshare in this consideration is in the regulator area Ar.
    When in this mode one describes the flow with the aim of creating the expression forthe soft opening in a pressure-flow diagram thus becomes:q = R * p1o, sWhere the flow resistance R of the entire throttling unit RU varies withthe kind according to the inventive idea described above.
    This can also be described as initially during the stroke p1 is substantially equalwith p2. This means that the pressure drop in the fixed third choke 6a is101520253014almost equal to zero in the first throttle. Thus, this means onepressure level which has a low value at opening but increases when the flow increases. Whenthen the pressure p2 drops in the second volume V2 the pressure drop increases due toof the first flow resistor RS1 at the same time as the pressure drop across itthe second throttle 5a decreases as the pressure drop p1-p2 over the solidthe choke 6a increases.
    This means that the valve both opens and closes with a gentle movementbecause the opening and closing pressure is low at the beginning of the stroke tofinally achieve the desired value.
    Figure 3c shows an alternative embodiment of the third choke 6a. Herethe contact between the second volume V2 and the upstream takes place directlyarranged the volume Vu through a hole in the form of a gap extending therefromsecond V2 to the first volume V1. The column has a height H and a width Bwhich forms an alternative design of the fixed area Af '= pi / 4 * d32 throughthat Af ”= B * H. Thus, even with this embodiment, the thirdthe equivalent diameter d3 of the choke 6a is calculated by usingthe above assumption that the throttling is circular. Of course can alsothis choke be arranged as a hole extending through the seat 2 fromthe first V1 to the second volume V2.
    Figure 4 shows a first embodiment of the invention where a simplified sketchof a pressure regulator in the form of a valve 1, mainly intended to adjustthe pressure of a damping medium flow in a shock absorber, isThe pressure regulator here preferably operates as a non-return valve.
    The damping medium flow is created by a movement in a shock absorber which creates onepressure difference across the main piston, in Figure 4 called HP, as parts ofthe shock absorber in two damping chambers. The pressure regulator according to the figures caneither be of a first variant and be placed on the main piston orof a second variant and placed at another unit that delimits the flowbetween the damping chambers. Here too, an adjusting part 3 works against a seat 2 whichillustrated.101520253015comprises a first, second and third choke 4a, 5a, 6a. The openingthe regulating forces are counteracted here by a spring 7.
    Figure 5 shows an example of a pilot-controlled valve. The valve has a valve housing 8and an axially movable first adjusting member 3. The axially movable firstthe movement possibilities of the adjusting part 3 are stopped by the seat part 2 which can beintegrated in or separated from the valve body 8. When the valve is open flowsthe damping medium Q1 from the upstream volume V., to thedownstream, the volume Vd arranged in that passage with a variableflow opening s created between the adjusting part 3 and the seat part 2. The valveis a two-stage, pilot-controlled valve, which means that the force that opensthe main valve is dependent on the pilot pressure generated in a pilot chamberVp. A part of the damping medium flow Q1 flows through an inlet hole inthe adjusting part 3 and the seat part 2 to the pilot chamber Vp so that it is on the adjusting partopposing pressure increases. Thus, in this case, the total of the valve is balancedregulating force Fr of an opposing sum force Fa created by spring forcesFrom the spring 7, any additional flow and frictional forces plus thoseforces Fp as a pilot pressure Pp in the pilot chamber Vp creates.
    Figures 6a-d show alternative embodiments of the seat part 2 with differentgeometries that provide the same function.
    Figures 6a and 6b show a plan view of the seat part 2 where the first and thethe second seat 4, 5 with its respective volume V1, V2 has the shape of part of asector. The circumference 04, 05 as the seats 4, 5 and thus alsothe throttles 4a, 5a have can also be defined as an equivalent diameterd1 and d2, respectively, this is done with the formulas:m = o4, / pi; az = osrpiThe throttles 4a, 5a have in Figure 6a been arranged partly in two groups orthrottling units RU symmetrically around the center line consisting of twoparagraphs first and second volumes V1, V2 and seats 4, 5. l Figure 6b is101520253016the throttles arranged in asymmetric groups or throttling unitsRU with two pieces first and second volumes V1, V2 and seats 4, 5 plus onefirst volume V1 and seat 4. The third choke 6a is in both figure 6a and6b is connected to the volume V2 of the second seat 5 and preferably hasthe shape of a heel with diameter d3.
    Figure 6c shows another embodiment of the soft opening function where itfirst and second seats 4, 5 with their respective volumes V1, V2 form onethrottling unit RU and the respective seat have the shape of a part of a circlewith diameters d1 and d2. The first seat diameter d1 is slightly heresmaller than the second seat diameter d2 in order to optimizethe damping properties of the shock absorber valve. Here, too, is the thirdthe choke 6a is connected to the volume V2 of the second seat 5a and hasthe shape of a hole with diameter d3.
    The throttling units RU in Figure 6c are grouped into eight units andoptimized in terms of selection of the throttle diameters d1, d2 and d3 forcompression. In addition, eight choke units RU are located onopposite side 2b of the seat part 2 also these optimized in terms of selectionof the throttle diameters d1, d2 and d3, but now for return.
    Figure 6d shows a further alternative embodiment of the seat part 2 withdifferent geometries on the compression and return side 2a, 2b ofthe seat part 2. The throttling unit RU on the compression side 2a consists oftwo first throttles 4a with diameter d1 and circumference 01, one kidney-shapedsecond choke 5a with circumference 02 which is determined by groove width d2 and candefined as the equivalent diameter d2 as well as a fixed third choke6a with the diameter d3. Same design on the throttle units RUis also repeated on the return side 2b of the seat part but here the holes have asacts as the third choke 6a replaced by slots B andthe depth H extending between the first and second throttlesvolumes V1, V2. The third choke 6a can still be assumed to have one101520253017equivalent diameter d3 defined by its width and depth. Eachthrottling unit RU is preferably repeated four times on each side2a, 2b of the seat part 2.
    Figure 6e shows a further alternative embodiment of the seat part 2 withthe same type of geometry on the compression and return side 2a, 2b ofthe seat part 2. The throttling unit RU on both sides in this case consists ofa first cake piece-shaped choke 4a defined in surface and circumference throughangle an1, radius r1, diameter D1 and width b1 giving an equivalentdiameter d1 and circumference 01. The throttling unit RU also consists of acircular second choke 5a whose geometry is determined by groove width b2and the diameter D2 of the groove which can also be defined as the equivalentdiameter d2 with circumference 02 and also a fixed third throttle 6a withdiameter d3. The same design on the choke units RU is repeatedalso on the return side 2b of the seat part and here have the holes that function asthe third choke 6a the same geometry, however, individually adaptedextending between the volumes V1 of the first and the second choke,V2. The third choke 6a here has an equivalent diameter d3 the samewhich had d3 indicated in the figure. Each throttling unit RU has in this caseno repetition because there is a second choke 5a on the first eightthrottles 4a on each side 2a, 2b of the seat part 2. This example wantsshow how the invention can be allowed to vary in form over wide limits but stillclearly stay within the scope of protection of the claims.
    Figure 7 shows a double-acting pilot-controlled shock absorber valve with apressure regulator where flows are allowed in both the compression and return direction.
    The pressure regulator here has a seat part 2 and on each side of this onefirst and a second adjusting part Sa, 3b. Seat part 2 with its adjusting parts Sa, 3bare mounted between a first and a second main housing 10a, 10b in a holder11 delimited at its two ends by a first and a second cover 12a, 12b.
    This device is designed to be a part of the mainstay HP thatdelimits the shock chamber of a shock absorber, where the movement of the main piston in -101520253018in relation to a damping cylinder, it makes it adjustable by the valvethe damping media flow.In the first and second main housings 10a, 10b, one or more are arrangedplungers 13a, 13b intended to create a counter force in the form of a pilot compressive forceFp on the first and the second adjusting part 3a, 3b and symmetrically arrangedaround the holder 11. The plungers 13a, 13b also provide support for at least a first anda second main spring 14a, 14b which also create a restraining force Ffon the frame parts 3a, 3b. The spring force can be adjusted with spring holder 15a,15b. The total restraining force Fa defined by Fp + Ff balancesthe valve's total regulating force Fr which is created by the damping medium flow throughthe adjusting part, according to the function described above.
    The working range of the pressure regulator, ie the difference between the highest and lowestpressure, is determined by the number of plungers 13a, 13b which can be adapted to eachapplication. The design of the plungers 13a, 13b against the facing of the frame partpart is important for how the actuating part's 3 opening movement in relation toseat part 2 takes place. If the throttle units RU are placed symmetricallyon the seat part 2, the adjusting part 3 opens substantially parallel tothe seat part 2 and the plungers 13a, 13b. About the choke units RU insteadliftingto act on different points equallyare placed asymmetrically on the seat part 2 so they canthe regulating forces are said to be dividedasymmetrically placed on the seat part as the throttling units RU.
    Depending on the design of the plungers 13a, 13b, the adjusting part 3 can tip / tiltaround one or more of the plungers 13a, 13b so that when it opens hasthe adjusting part 3 an angle in relation to the seat part 2. This angle varieswith the stroke and with the damping fluid flow flowing throughthe throttling units RU. An damping of the movement of the plungers 13a, 13b canprovided, for example, by means of throttles 26 in a pilot flow channel21. The throttles 26 have been positioned to determine the size ofthe pilot flow menbcksà constitutes a damping for the movement of the plungers andhence the valve in its entirety.101520253019The plungers 13a, 13b may also be different in number on compression 2arespectively the return side 2b of the seat part 2 for the purpose of providing adouble-acting function and an asymmetry, eg so that the pressure level belowthe return stroke R becomes larger than during the compression stroke C. An asymmetrical oneplacement of the plungers 13a, 13b aims to create both the highest andminimum pressure levels and associated characters that meet customer requirements.
    In addition, the springs 14a, 14b inside symmetrically placed plungers 13a,13b be asymmetrically arranged with respect to bias andspring constant. Respective springs 14a, 14b may thus have different onesbias and spring constant. Also the number of plunges and the diameters ofthese can be used for the purpose of adjusting the size of the pressure level / working area.
    The seat part 2 is in this embodiment double-acting, which means that aor more of the combination of a first and a second volume V1, V2 withrespective first and second seats 4, 5 are arranged on both sides ofthe seat part. The first adjusting part 3a is arranged on the first of the seat partpage 2a, which may also be called its compression side, and itthe second adjusting part 3b is arranged on the other side 2b of the seat part, which cancalled its return page. The size of the first and second volumes variesaccording to the desired in the differentdamping property differences such asthe damping directions C, Ft.Figure 8a shows a side view of a part of the piston unit with the parts that areactive during a compression stroke C. The first volume V1 with its firstseat 4 with diameter d1 extends through the seat part 2 so that aflow path is created from the second 2b of the seat part to the first 2a side. The other onethe volume V2 is delimited at the other side 2b of the seat part but a flow pathis created from the second 2b of the seat part to the first side 2a by the thirdthe choke 6a with diameter d3 is arranged as a hole in the othervolume V2 pressure-affected surface.101520253020Figure 8b shows the parts of the piston unit which are active during a return stroke R. Denthe first volume V1 with its first seat 4 with diameter d1 extendsthrough the seat part 2 so that a flow path is created from the first 2a of the seat partto other 2b page. The second volume V2 is delimited at the seat partfirst side 2a but a flow path is created from the first 2a of the seat part to the secondside 2b in that the third choke 6a with diameter d3 is arrangedas a hole in the pressure-affected surface of the second volume V2.Figures 8a and 8b show that the first and second volumes V1, V2, whichcan be said to be arranged as a throttling unit RU, at least one is repeatedtime on the respective side 2a, 2b of the seat part. Extra is also shown herecut-outs 16 arranged at the seat part facing the respective sidesurface. These cut-outs 16 ensure that damping medium can flow into the respectivethrottling unit first V1 and second volumes V2, where the flow to the secondthe volume occurs through the third throttle 6. The flow in the direction that isparallel to the direction of impact is prevented by the adjusting parts 3a and 3b, respectivelywhich abuts and seals against both sides / surfaces 2a, 2b of the seat part 2.
    Figure 9 shows a pilot controlled shock absorber valve including itthe pressure regulator according to the invention and figures 10a and 10b show aschematic view of a shock absorber with a pilot controlled shock absorber valve andhow the damping medium flows during a return and a compression stroke, respectively.
    Explanation of the flow through the pressure regulator is explained on the basis of allthese three figures 9, 10a and 10b.Figures 10a and 10b show that the shock absorber's damping body is divided into onefirst and a second damping chamber DC1, DC2 of a compartment in shapeof a main piston HP attached to a piston rod. Movement of the main piston inthe damping cylinder creates a damping medium flow between the respectivedamping chamber via the shock absorber valve. The shock absorber valve can bearranged in the main piston or even in a separate space interconnectedwith the damping chambers DC1, DC2. The hydraulic damping medium that is101520253021arranged in the damping cylinder is pressurized with a gas pressure Pg to reducethe risk of cavitation in the damping medium, ie raising the cavitation pressure.In Figure 10a, the main piston of the shock absorber body moves in the return direction witha certain speed vf and compresses the first damping chamber DC1 orthe return chamber. The damping medium in the first damping chamber DC1 then receivesthe pressure Pr which is higher than the pressure Pc in the second damping chamber DC2.
    This pressure acts on both sides of the plunger 13a which is thus held onplace of the spring 14a and on the first side 2a - the return side - ofthe seat part 2, which partly means that the first adjusting part 3a is pressed closedtowards its seat 2a but also partly that the second adjusting part 3b opens a certainstroke s which depends on the main piston speed v ,. The damping medium then flowsthrough the pressure regulator via the first, third and second throttles 4a, 5a,6a which contribute to the second adjusting part 3b lifting from the seat part by onesoft movement. The lifting regulating forces as the pressure in the damping chamberscreates is counteracted by a spring force Fs created by the main spring 14b and bya pilot force Fp created by a pilot pressure Pp. The spring force Fs and the pilot forceFp acts both via the respective plunger 13a, 13b on the second adjusting part 3b.
    The pilot force Fp is created by a flow going from the firstthe damping chamber DC1 through a first upstream check valve 17 in the firstthe lid 12a of a first inlet pilot volume Vip1 arranged between the firstthe lid 12a and the first plunger (s) 13b.
    The pilot pressure Pp is built up in the inlet pilot volume Vim through the pilot flowbetween the first and second damping chambers DC1, DC2 and adjustedvia an ECU-controlled continuous electrical signal that controls the power supply to asolenoid 18 which regulates the position of a pilot slide 19 relative to onepilot valve seat 20 in a main pilot volume Vhp. An adjustable flow openingarranged to restrict the damping fluid flow is created between the pilot valve seat 20 andpilot slide 19. Thus, it works according to existing operating principlesdescribed in EP 0 942195. The flow opening size and the pilot slide 19101520253022position in the main pilot volume Vhp is determined by a force balance on the pilot slide19. The power balance is mainly created by the sum of the actuating force fromthe solenoid 18 and any additional spring forces and the like against actionof the resistance dependent on the pressure in the inlet pilot volume Vipregulator power Fr.inlet pilot volume Vim is connected to the main pilot volume via afirst pilot flow channel 21 arranged in the holder 11. The pilot damping medium flowsfirst downstream check valvethen via a 22 through a secondpilot flow channel 23 in the holder 11 to the second damping chamber DC2.the main piston inFigure 10b movesthe compression direction at a certain speed vc and compresses itthe shock absorber body insecond damping chamber DC2. The damping medium in the other damping chamberDC2 then receives the pressure Pc which is higher than the pressure Pr in the firstdamping chamber DC1. This pressure acts on the other side 2b ofthe seat part 2, which means that the first adjusting part 3a opens a certain strokes which is dependent on the main piston speed vc. The damping medium then flowsalso here through the pressure regulator via the first, third and second 4a, 6a, 5athe choke. The lifting regulating forces as the pressure in the damping chamberscreates is counteracted by a spring force Fs created by the first main spring14a and by a pilot force Fp created by the same pilot pressure Pp as viathe plunger (s) 13a act on the first adjusting part 3a.
    In this figure, the pilot flow through the second damping chamber C2 passes througha second upstream check valve 24 in the second cover 12b of a secondinlet pilot volume Vipz arranged between the second cover 12b and thethe second plunger (s) 13a. The second inlet pilot volume Vrpi isconnected to the same main pilot volume Vhp via the same firstpilot flow channel 21 arranged in the holder 11. The pilot damping medium then flowsvia a second downstream valve 25 directly to the firstdamping chamber DC1.1015202523The shock absorber valve is functionally symmetrical, which means thatdownstream and upstream change places during the movement of the piston. In additionthe valve comprises a large number of parts which are repeated in order to hold downcost and number of unique details.
    To facilitate the main assembly, the main valve package can also be includedits main piston HP is riveted together into one unit. This is preferably done in aside mounting. This unit is shown in Figure 7 where the holder 11 is rivetedat its lower end to hold the piston parts in place. The device can alsoinclude a version of the main valve package where the solenoid and piston areintegrated or a version where the valve outer housing and piston areintegrated. The main valve package is preferably the assembly of anut that tightens the valve package and provides prestressing and sealing to onenumber of parts in the valve. Thanks to this bias voltage, none are neededsoft seals, which benefits the compact and cost-effective designwhich is sought.
    The invention is not limited to that of the above by way of exampleshown embodiment but can be modified within the scope of the followingclaims and the inventive concept. For example, this invention maycan also be used in other types of shock absorber valves, mounted in orseparated from the main piston.
    权利要求:
    Claims (10)
    [1]
    Pressure regulator (1) intended to adjust the pressure of a total damping fluid flow (q) between an upstream and downstream arranged volume (Vu, Vd) with a first and a third pressure (p1, p3) in a shock absorber valve where the pressure regulator comprises an adjusting part ( 3) which moves with an axial stroke (s) relative to a seat part (2) with a first side (2a) comprising at least a first and a second seat (4, 5) in such a way that one with the stroke (s) varying flow opening is created between the adjusting part (3) and the first and the second seat (4, 5) and where the flow opening is arranged to restrict the total damping medium flow (q) between the upstream and downstream arranged volumes (Vu, Vd), characterized by that the seat part (2) comprises at least two first and second throttles (4a, 5a) arranged in parallel, the flow restricting ability of which is determined by the design of the seats (4, 5) and a fixed third throttle (6a) arranged in series with the second throttle (5a) where first and second throttles (4a, 5a) varies with the stroke (s) so that through the first restriction there is a first damping medium flow (q1) and through the second and the third throttling there is a second damping medium flow (q2) where the ratio (pt / p3) between the first (pt) and the third pressure (p3) and the ratio (q1 / q2) between the first (qt) and the second damping medium flow (q2) increase with increasing stroke (s).
    [2]
    Pressure regulator (1) according to claim 1, characterized in that the first and the second choke (4a, 5a) are defined by a first (d1) and a second seat diameter (d2) which is equivalent to the respective circumference of the choke (04, 05). ) so that the choke (4a, 5a) can be assigned different geometric shapes based on the defined circumference (04, 05).
    [3]
    Pressure regulator (1) according to claim 1 or 2, characterized in that the first and the second choke (4, 5) vary with the stroke (s) in that their curtain areas depend on the choke diameter (dt, d2) and the stroke (s). (Asi, As2) increases and transmits a larger flow of damping medium with the stroke while the third fixed serially arranged throttle (6) ensures that the second damping medium q (q2) is throttled more than the first damping medium flow (q1) .
    [4]
    Pressure regulator according to claim 2 or 3, characterized in that the first side (2a) of the seat part (2) has cut-outs arranged inside the circumference (04, 05) of the first (4) and the second seat (5) which create first and second volumes. (V1, V2) arranged in the seat part (2) whose, with the circumference equivalent, diameter (d1, d2) defines pressure-affected regulator areas (Ar1, Ar2) on the adjusting part (3).
    [5]
    Pressure regulator (1) according to claim 4, characterized in that the third throttle (6a) is formed as a hole with a third equivalent diameter (d3) which is arranged in the seat part 2 and which creates a flow opening between the upstream volume ( Vu) and the second volume (V2).
    [6]
    Pressure regulator (1) according to claim 4, characterized in that the third choke (6a) is designed as a hole with a third equivalent diameter (d3) extending between the first and the second volume (V1, V2) -
    [7]
    7. Pressure regulator (1) according to claim 6, characterized in that the third throttle (6a) is designed as a catch with a certain width (B) and a certain depth (H).
    [8]
    Pressure regulator (1) according to one of Claims 4 to 7, characterized in that the first and the second volume (V1, V2) together with the throttles (4a, 5a, 6a) are arranged as a throttling unit (RU) which is repeated at least a thread on the first side (2a) of the seat part (2). 10 15 20 25 I 12. 26
    [9]
    Pressure regulator (1) according to claim 8, characterized in that the seat part (2) also has a second side (2b) opposite the first side (2a) on which one or more throttling units (RU) are arranged.
    [10]
    Pressure regulator (1) according to one of the preceding claims, characterized in that the regulator is intended to adjust the pressure (p1) of the total damping medium flow (q) between a first and a second damping chamber (DC1, DC2) divided by a delimiting part (HP) which moves at a speed determined by the design of the surroundings in a damping unit. 1 1. the damping medium (q) is arranged to be able to flow through the pressure regulator via the pressure regulator (1) according to claim 10, characterized in that the first throttling units (RU) in a direction from the first (DC1) to the second damping chamber (DC2) and also in a direction from the second (DC2) to the first damping chamber (DC1) through the second throttling units (RU). Pressure regulator (1) according to claim 11, characterized in that the pressure regulator is arranged mounted directly in the section of the shock absorber (HP) 13. The pressure regulator is arranged in a separate space connected to the damping chambers (DC1, DC2). Pressure regulator (1) according to claim 11, characterized in that
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    同族专利:
    公开号 | 公开日
    EP2422109B1|2013-11-06|
    CN102459943B|2014-10-22|
    CN102459943A|2012-05-16|
    EP2422109A1|2012-02-29|
    US20120097493A1|2012-04-26|
    WO2010122102A1|2010-10-28|
    SE533996C2|2011-03-22|
    JP2012524876A|2012-10-18|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE0900543A|SE533996C2|2009-04-23|2009-04-23|Pressure regulator in a shock absorber valve|SE0900543A| SE533996C2|2009-04-23|2009-04-23|Pressure regulator in a shock absorber valve|
    PCT/EP2010/055344| WO2010122102A1|2009-04-23|2010-04-22|Pressure regulator for shock absorber|
    JP2012506500A| JP2012524876A|2009-04-23|2010-04-22|Pressure regulator for shock absorber|
    EP20100717596| EP2422109B1|2009-04-23|2010-04-22|Pressure regulator for shock absorber|
    CN201080026428.3A| CN102459943B|2009-04-23|2010-04-22|pressure regulator for shock absorber|
    US13/265,977| US20120097493A1|2009-04-23|2010-04-22|Pressure regulator for shock absorber|
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