DE3332535A1 - Vibration damper arranged between the transmission block and the shift linkage of a motor vehicle - Google Patents

Abstract

The aim in a hydraulic vibration damper arranged between the transmission block and the shift linkage of a motor vehicle is to ensure in conjunction with virtually no increase in the shifting forces that jumping out of the engaged gear is prevented. For this purpose a valve comprising at least one valve seat and at least one closing element preloaded into an open position away from the valve seat is arranged in the duct of the piston provided with a larger cross section, which valve presents in the open state only a slight, preferably negligible resistance to the hydraulic fluid flowing through in the event of transmission vibrations and around the closing element of which hydraulic fluid flows against the preloading force in such a way that above a predetermined rate of flow, directed counter to the preloading force and determined by the excessive transmission vibrations, of the hydraulic fluid flowing through the valve the dynamic force acting on the closing element due to the correspondingly increasing dynamic pressure becomes supercritical and overcomes the preloading force.

Description

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The invention relates to one between the gear block and the Shifter linkage of a motor vehicle arranged vibration damper with one filled with hydraulic fluid on his Bottom cylinder with a mounting connector and a piston that divides the cylinder in two divides a channel connected working spaces and which is attached to a piston rod, which is closed by a cylinder Lid is passed through tightly and has a fastening connector at its outwardly protruding end. -

It is already "known that if the vehicle transmission shakes heavily in the direction of travel, the shift linkage does not always follow these movements in the same direction due to its inertia, which means that gears that are engaged can jump out of their own accord while driving. This process is called gear jumping It is already known to use vibration dampers with pistons arranged in a cylinder which, due to their structure and damping characteristics, force the shift linkage to follow the movements of the gearbox prevents gear jumping almost completely, but has the disadvantage that when shifting, where there must be a relative movement between gear and linkage, higher forces have to be applied in order to shorten or lengthen the damper just the other way around, ie _r di The risk of gear jumping is hardly reduced, but the shifting forces are only slightly increased.

In known vibration dampers, a compromise must always be made between the switching forces that are to be kept as small as possible and find the most complete avoidance of the gear jump, which ultimately leads to the shifting forces are larger than desired and still occasionally jumps in gait.

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The aim of the invention is now to provide a vibration damping of the type mentioned at the outset, with which the switching forces jump out when the switching forces are practically not increased of the gear engaged practically no longer occurs.

To solve this problem, the invention provides that a valve consisting of at least one valve seat and at least one closing body biased away from the valve seat into an open position is arranged in the channel provided with a larger cross-section, which valve is only open to the hydraulic fluid flowing through with transmission vibrations opposes a low, preferably negligible resistance and the closing body is flowed around against the biasing force of the hydraulic fluid such that above a predetermined, directed counter to the biasing force flow rate "of the current flowing through _n · the valve hydraulic fluid v on the closing body due to the corresponding increase in dynamic pressure > Effective damming force becomes supercritical and the «pre-tensioning force is overcome.

Due to this design, the closing body only moves in the closing direction due to the hydraulic fluid of the back pressure and thus interrupts the hydraulic fluid flow by closing a hole, if through-strong Shaking movements of the gearbox the oil speed has reached a certain value. This value should be appropriate about twice as high as the value that is achieved with fast, sporty gear changes. The predetermined flow rate is therefore expediently the one that causes transmission vibrations when there is a risk of gear jumping out of the gear occurs, while at the flow velocities caused by sporty viewing the closing body should not yet be able to move into the closed position.

According to a first embodiment, a spring is provided to generate the biasing force in the valve, which is located between

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the closing body and the valve body extends.

It is also possible that to generate the pretensioning force a magnet fixed relative to the valve body is provided and the closing body is designed to be magnetic.

While it is basically conceivable that the vibration damper only acts on one side by only one closing body and edm valve seat is provided, it is preferred if the VentJul two on opposite sides of the closing body having arranged valve seats and the closing body by two oppositely acting biasing forces in its between the two valve seats located open position or by one either in one or the other. direction acting supercritical damming force is pressed on each of the two valve seats. In this embodiment so in the case of the. Jumping out of gear enables the oscillation amplitude and speed of the flow path interrupted in either direction.

An advantageous further development of the invention is characterized in that the valve is two one behind the other in the direction of flow having spaced-apart closing body, which with on the sides facing away from each other or between You intended valve seats cooperate. In this way it is possible to use the closing body and valve seats as well as those who charge them. Optional preload forces to train the same or slightly different, to optimize the arrangement for a specific application.

In the aforementioned embodiment, it is useful if on the sides of the closing body facing or facing away from one another, the closing body is reached until it is reached The critical damming force in the open position holding a flow path are provided magnets. Through this the desired sudden response of the vibration damper when the critical accumulation force is exceeded will.' .

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In the simplest case, each closing body of the valve is as formed around the flowed ball.

But it is also possible for the closing body to have at least one piston slide which can be displaced in a cylinder bore an axially through bore and cooperating with the valve seats on the opposite end faces provided 'closing body is. The piston valve biased towards the open position by disc springs arranged between its end faces and the valve body be.

The channel connecting the two working spaces is generally arranged in the piston. However, it can also be in the cylinder housing be provided if the accommodation is due to the increased space required by the valve according to the invention should be problematic in the piston itself.

It is particularly advantageous if the mass of the closing body and the spring constant of the helical spring are chosen so that the natural frequency of the vibration system closing body helical spring on the gear jumper-defeating transmission vibration is matched. Due to this design, the valve works in resonance with the particularly unpleasant gear vibration, so that an optimal jumping back and forth of the closing body or the closing body between the two Closed positions or between closed and open positions is achieved.

The invention is described below, for example, with reference to the drawing; in this shows:

1 shows a schematic view of a shift linkage arranged on a transmission block with the inventive one Vibration dampers,

Fig. 2 is a partially sectioned side view of a first

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Execution of a vibration damper according to the invention,

FIG. 3 shows an enlarged detail from FIG. 2 for illustration of the valve according to the invention,

Fig. 4 is a section along line IV-IV in Fig. 3,

Fig. 5 is a partially sectioned side view of another Embodiment of the vibration damper according to the invention ,

6 shows a section along line VI-VI in FIG. 5,

7 shows a partially sectioned side view of a third embodiment of the vibration damper according to the invention with the valve open,

FIG. 8 shows the same view as FIG. 7, but with the valve closed,

9 shows an enlarged detail from FIG. 8 for a better illustration of the valve according to the invention,

Fig. 10 is a section along line X-X of Fig. 9,

11 shows a further embodiment of the in accordance with the invention Vibration damper valve used in a partially sectioned side view analogous to FIG. 9,

Fig. 12 shows a further embodiment of a for an invention appropriate valve in the open position and in accordance with the vibration damper

Fig..13 is the same partially sectioned side view as Fig. 12, but with the valve closed.

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Fig. 1 shows a schematic, partially sectioned side view the gearshift at 30 of a motor vehicle that has a shift linkage 31 is connected to the transmission block 32 of the vehicle.

Extends between a bearing block 35 attached to the gear block 32 and a bearing block 34 arranged on the shift linkage 31 a vibration damper 33, which is correspondingly shortened when shifting movements of the shift linkage 31 or lengthened and dampen vibrations between the shift linkage 31 and the transmission block 32 so that they jump out A gear is prevented by opposing oscillations of the shift linkage 31 and the transmission block 32 will. According to FIG. 1, the vibration damper 33 is attached by means of the fastening connection arranged on the cylinder base. Piece 36 or by means of its piston rod 37 attached to the bearing blocks 34 and 35 via universal joints 58 and 59, respectively, in order to be able to absorb movements occurring essentially perpendicular to the extension of the shift linkage 31. Essential is that the vibration damper according to the invention is not in the ■ Shift linkage 31 used, i.e. one behind the other with him, but is connected in parallel to this.

According to FIG. 2, the vibration damper 33 according to the invention a cylinder 26 open on one side with an axially displaceable one therein Piston 24, the piston rod of which extends through the bottom 38 of the cylinder in the direction of the gear block 32 or of the shift linkage 31 extends. The piston rod 37 is passed through an opening 39 in the base 38 in a sealed manner.

The opposite end of the cylinder is closed by a cover 60 on which the fastening connector 36 for the attachment to the transmission block 32 or the shift linkage 31 is arranged.

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According to the invention, the piston has a relatively large thickness in order to be able to move in a continuous axial channel 11 formed therein To be able to accommodate a valve 12 with a relatively large diameter, which valve consists of a fittingly and firmly arranged in the channel 11 Valve body 17, 17 '(see also Fig. 3, 4) with valve seats 14,14 ', a closing body 13 designed in the form of a ball and these from opposite directions acting helical compression springs 16,16 '.

The valve body 17, 17 'has a through the piston Channel, which from bores 40, 40 'at both ends of the valve body 17, 17', adjoining it, widened Receiving spaces 41,41 'for the two helical compression springs 16,16' and flow passages 42 arranged around the ball 13. Between the flow channels 42 there are webs which axially connect the closing body 13 in the circumferential direction 17 ″, which hold the ball in the radial direction, so that it only moves axially relative to the valve channel or the bore 11 can perform.

The helical compression springs 16, 16 'are dimensioned and arranged in such a way that that they normally hold the ball 13 in the central position shown in FIGS. 2 and 3, in which the arranged in the cylinder Hydraulic fluid 15 can flow through the valve 12 along the path indicated by dashed lines.

If the piston rod 37 moves in Fig. 2 in the direction of arrow f, the hydraulic fluid 15 flows in the direction of arrow F through the valve; when the piston rod 37 moves in the opposite direction the direction of flow is also reversed accordingly.

The vibration damper shown in FIGS. 2 to 4 works as follows:

Up to a predetermined flow rate of the hydraulic fluid 15 through the valve 12 the hydraulic fluid

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Liquid flow practically no or only a very small amount Opposite resistance. The flow channel 40, 41, 42, 41 ', must be dimensioned accordingly with regard to the flow cross-section.

However, it becomes that predetermined flow rate exceeded within the valve 12, which occurs from the moment when there are vibrations generating gear jump, so is the back pressure acting on the ball 13 the biasing force of the helical compression springs 16, 16 'overcome and the closing body 13, which has the shape of a ball, rests in a sealing manner against one of the valve seats 14, 14 '. In at this moment, the hydraulic fluid flow rate becomes suddenly reduced to zero, so that the back pressure also disappears and the ball 13 through the Biasing force of one of the springs 16, 16 'back into its central position is shifted because the static pressure is much smaller than the force of the progressively tensioned compression spring. After closing, the valve 12 opens again immediately, at a speed that is determined by the static pressure, the mass of the ball 13 and the biasing force of the springs 16,16 'is determined.

Now comes the gear vibration in with a movement in half-period connected in the opposite direction, then finally through the half-period which acts in the opposite direction Damage force brought the valve ball 13 to the opposite valve seat -.14 .. or 14 *, and the closing-opening clearance repeats itself anew in the opposite direction.

Around this periodically repeating with the transmission oscillation Optimizing the opening and closing process is what it should do from the closing body 13 and the helical compression springs 16, 16 ' existing vibration system by suitable design of the shooting body mass and the spring characteristics to the gear jump generating Gearbox vibration be matched, -which z.3. one

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- 13 has a frequency of approximately 12 Hz. YYYZoYY

If, for example, the gear block 32 or the piston rod 37 moves to the left in FIGS. 1, 2, then at If the critical dynamic pressure is exceeded, the closing body 1-3 moves to the right, while the gear block moves .32 or the piston rod 37 to the right, the closing body 13 a movement to the left on its valve seat 14 to executes ·.

In the following figures, like reference numerals denote corresponding ones Parts as in the exemplary embodiment according to FIGS. 1 to 4.

According to Fig. 5, 6, the piston 24 is in the usual way without any Bores formed relatively thin. Instead, in addition to the cylinder 26, there is a channel 11 'in the cylinder housing in parallel therewith TO arranged, which for manufacturing reasons is the same length as the cylinder 26 and has bores 43 or 44 is in flow connection with the working spaces on both sides of the piston 24. The valve according to the invention, which has been described with reference to FIGS. 2 to 4 is located in this embodiment within the axial Channel 11 * between the bores 43, 44. It works completely analogous to the valve described with reference to FIGS. 2 to 4

The channel 11 'is at the two end faces at the level of the cylinder base 38 or of the cylinder cover 60 closed by plugs 45.

All damper versions must be above the hydraulic fluid 15 still air cushions 46 are provided to the To influence damping properties of the vibration damper 33 according to the invention and too abrupt decelerations in the To avoid the event of a closure of the valve 12 and around to compensate for the different piston rod volume when the rod is extended and retracted.

2 and 5 are the two extreme positions of the piston 24 once in full lines and the other in

dashed lines illustrated.

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FIGS. 7 and 5 show an exemplary embodiment similar to that according to FIGS. 5, 6, but with a bypass channel 11 ′ with a permanent magnet 18 working valve. 12 after the Figures 9 and 10 is used.

According to FIGS. 9 and 10, the valve body 17, 17 'again narrow inlet bores 40, 40 'at both ends, then subsequently however, already the valve seats 14,14 '. The expanded receiving spaces for the springs 16, 16 'are omitted so here.

immediately following the valve seats 14,14 'are two balls 13, 13 'each having an axial spacing and each forming a closing body movable in the axial direction, arranged, which cooperate with the valve seats 14,14 *.

A permanent magnet 18 is located in the space between the closing bodies 3, 13 ', which are designed to be soft magnetic. which has the apparent from Fig. 10 flat cross-section to next to him the side channels 42 for the unhindered Allow hydraulic fluid to pass through.

Because of this training, the balls 13, 13 'are below the critical flow velocity held by the permanent magnet 18 in the open position shown in FIGS. 7 and 9.

Now becomes the critical flow rate of the hydraulic fluid exceeded by the valve 12, e.g. in the direction from left to right in Fig. 8, the pressure on the ball 13 ' acting damming force to release the ball 13 'from the magnet 18 and press it against the valve seat 14'. As soon as the direction of movement is reversed in the course of the oscillation, the ball 13 'is released again from its seat 14' and comes to rest on the magnet 18, where it is held. Correspondingly, the other ball 13 then detaches from the magnet 18 and rests against the left seat 14.

The working cycle is therefore in principle the same as in the exemplary embodiment according to FIGS. 2 to 4.

The valve 12 according to FIGS. 9 and 10 could also be arranged in the piston 24 as according to FIG.

In the embodiment according to FIG. 11, the seats 14, 14 'are in the middle of the valve body 17,17 * arranged and through a connecting hole 42 'connected. The the closing body forming balls 13,1.3 'lie on opposite sides Sides to the "seats 14, 14 '" when the corresponding dynamic pressure is applied, and in doing so they break away from on opposite sides Sides like the valve seats 14,14 'arranged permanent magnets 18.18 *, which in cross section is similar to that of the embodiment according to Figure 10 are designed to allow the flow of hydraulic fluid laterally. Basically the valve 12 according to FIG. 11 works in the same way as that according to FIG. 9.

FIGS. 12 and 13 show one in both a piston channel 11 as well as in a cylinder channel 11 'to be arranged embodiment of a valve 12, which again has a valve body 17, 17 'with input bores 40, 40'. Inside the inlet holes 40, 40 ', the valve body 17, 17' expands like a cylinder by a piston slide within the cylinder bore 19 20, which is traversed by one or more axial bores 21.

The closing bodies 13, 13 'in the form of valve disks project axially from the end faces of the piston slide 20 in order to work together with valve seats ^{14, 14' provided at the inner ends of the inlet bores 40, 40 1.}

Between ring steps 22,22 'and the end faces of the piston valve 20 disk springs 16, 16 'are arranged, which, similar to the helical compression springs according to FIGS hold in a central position.

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Below the critical flow speed, the hydraulic fluid flows in the direction indicated by arrows in FIG. 12 Direction largely unhindered by the valve 12 and in particular the axial channels 21 therethrough. However, after the critical flow velocity has been exceeded, the piston slide valve 20 in one direction or the other by the dynamic pressure occurring on one of its end faces against the Shifted force of the opposite plate spring 16 or 16 ', for example in the position according to Fig. 13 / where the right plate spring 16 'is pressed flat and the closing body 13 · is open the valve seat 14 'rests. Also the way this valve works thus corresponds to the previous embodiments.

For assembly reasons is in the embodiment according to 12 and 13 of the closing bodies 13, 13 'each on a closing pin 23 or 23 'arranged, which is pressed into a central bore 25 of the piston valve 20 from opposite sides are.

It is further provided according to the invention that the inlet bores 40, 40 * in cylindrically designed valve seat supports 27,27 'are formed, which in corresponding bores 28,28' of the valve body 17,17 'are pressed in flush.

To reduce the flow of hydraulic fluid as little as possible to hinder, holes 29,29 'are provided in the disc springs.

In the embodiments according to FIGS. 8 to 13 is a It is therefore not necessary to coordinate the closing body mass or the characteristic curve of the disc springs with the gear vibration. because the disc springs 16,16 'and the magnets 18,18' When the valve 12 is closed, only a very small return force is exerted on the due to its strongly degressive characteristics Exercise closing body. This is chosen so that it is smaller than the static one that is present when the valve is closed

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Pressure. The closing body 13 , 13 'thus only detaches itself from the sealing surface and goes into its rest position when the transmission oscillation is reversed. Then the second closing body responsible for this direction seals and the process is repeated.

A preferred inventive idea can therefore also be seen in that the closing body 13,13 'holding in their rest position Biasing forces upon movement of the closing bodies 13, 13 'in Direction of the valve seats 14,14 'fall sharply degressively to the to achieve the effect described above.

It is important that if the valves are not closed, a sufficient large passage cross-section is present in valve 12, so that the hydraulic fluid flow when the valve is open practically no resistance is opposed.

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Claims (1)

OPEL September 6, 1983 8045 Applicant: Adam Opel Aktiengesellschaft, Rüsselsheim Vibration damper arranged between the transmission block and the gearshift linkage of a motor vehicle Patent claims ν j Between the gear block and the gearshift linkage of a motor vehicle "arranged vibration damper parallel to the gearshift linkage, with a cylinder filled with hydraulic fluid and provided with a fastening connector at its bottom, and with a piston that divides the cylinder into two working spaces connected by a channel and the "is attached to a piston rod which is passed tightly through a cover closing the cylinder and has a fastening connection piece at its outwardly protruding end, characterized in that in the channel (11, 11 ') with a larger cross-section, one of at least one valve seat (14, 14 ') and at least one of the valve seat (14, 14') biased away into an open position closing body (13, 13 ') existing valve (12) is arranged, which the hydraulic fluid flowing through when the transmission vibrations in the open state. , only a minor, preferably negligible .entgegensetzt gbaren resistance and the closing body is flowed around against the biasing force of the hydraulic fluid in such a way (13,13 ') that is above a predetermined, directed counter to the biasing force _f by excessive Getriebeschwingunqen related flow rate of the hydraulic fluid flowing through the valve (12) which on the closing - COPY body (13, 13 ·) due to the correspondingly increasing dynamic pressure effective damming force becomes supercritical and overcomes the pretensioning force. 2. Vibration damper according to claim 1, characterized in that the predetermined flow rate is that which occurs when there is a risk of gear vibrations causing gear disengagement, 3. Vibration damper according to claim 1 or 2, characterized in that for generating the A spring (16, 16 ') is provided for biasing force in the valve which extends between the closing body (13, 13 ') and the valve body (17, 17'). 4. Vibration damper according to claim 1 or 2, characterized in that for generating the biasing force at least one fixed relative to the valve body ™ (17, 17 ') Magnet (18, 18 ') is provided and the closing body (13, 13') is magnetic. 5. Vibration damper according to one of the preceding claims, characterized in that it is marked. ensure that the valve (12) has two valve seats (14, 14 ') arranged on opposite sides of the closing body (13, 13') and the closing body (13, 13 ') by two oppositely acting biasing forces in his.- between the two valve seats (14, 14 ') located open position or by a supercritical damming force acting either in one direction or the other each one of the two valve seats (14, 14 ') is printed. 6. Vibration damper according to one of claims 1 to 4, characterized characterized in that the valve (12) is two spaced apart in the flow direction one behind the other Closing body (13, 13 ') which is provided with on the sides facing away from one another or between them. Valve seats (14, 14 ') interact. 7. Vibration damper according to claim 6, characterized in that on the facing or sides of the shooting bodies facing away from one another (13, 13 ") the shooting bodies (13, 13 ') until the critical Magnets (18, 18 ')' that hold a flow path and hold a dam force in the open position are provided. 8. Vibration damper according to one of the preceding claims, characterized in that each shooting body of the valve is designed as a ball (13, 13 ') with a flow around it ". 9. Vibration damper according to one of claims 1 to 7, characterized in that the shooting body a piston slide (20) which can be displaced in a cylinder bore (19) and has at least one axially continuous Bore (21) and with the valve seats (14, 14 ') cooperating on the opposite end faces provided closing bodies (13, 13 '). 10. Vibration damper according to claim 9, characterized in that the piston slide (20) through between its end faces and. the valve body (17, 17 ') arranged disc springs (16, 16 ') towards the open position. is biased. 11. Vibration damper according to one of the preceding claims, characterized in that the channel (11) connecting the two working spaces is arranged in the piston (24) is. 12. Vibration damper according to one of claims 1 to 10, characterized characterized in that the channel (11 ') is arranged in the cylinder housing. 13. Vibration damper according to one of the preceding claims, characterized in that it rejects the mass of the closing body (13) and the spring constant of the helical spring (16, 16 ') - are chosen so that the natural frequency of the vibration system closing body coil spring on the COPY -A- Gear jump generating gear vibration: is matched. Vibration damper according to one of Claims 1 to 12, characterized in that the holding force for the shooting body (13, 13 ') when released from the rest position decreases degressively, i.e. up to Reaching the valve seat (14, 14 ') practically collapses. COPY