DE3332535C2 - Vibration damper - Google Patents

Abstract

In the case of a hydraulic vibration damper arranged between the transmission block and the shift linkage of a motor vehicle, the aim is to prevent the gear engaged from jumping out of the gear engaged when the shifting forces are practically not increased. For this purpose, a valve consisting of at least one valve seat and at least one closing body pretensioned away from the valve seat into an open position is arranged in the larger cross-section of the piston, which in the open state only has a low, preferably negligible resistance to the hydraulic fluid flowing through when the transmission vibrates and the closing body of the hydraulic fluid flows around it against the biasing force in such a way that above a predetermined flow rate of the hydraulic fluid flowing through the valve, directed against the biasing force and caused by excessive gear vibrations, the damper force acting on the closing body due to the correspondingly increasing dynamic pressure becomes supercritical and the biasing force overcomes.

Description

δ 3 - 4

ί valve seats a further preferred embodiment of the invention designed as an inertia body

'IE closing body has this design of the closing provided that the two working spaces

Ir body has the effect that the valve is only arranged depending on the binding channel in the cylinder housing

'U acceleration force acting on the closing body This allows the accommodation of the one increased

Vj th and not depending on the displacement 5 th space requirement, according to the invention

Ji speed of the piston is operated. Simplify valve.

/ ,; Such a shock absorber is therefore to prevent the use of magnets according to the invention

': ■': ■ tion of gear jumping in a motor vehicle to pretension the closing body in their rest position

The drive is completely unsuitable because this valve has the effect that only a very low return force is dependent

f ' ability of certain driving situations - such. B. BE io is exercised on the closing body when this is in

■ accelerating, braking, or cornering - are already in their closed position. The return force is

■ Close V and thus a required switching advance is then less than that when the valve is closed.

v can prevent gang. dene static pressure, so that the closing body only

;; To the ease of use and driving safety can then return to its rest position, if

: ■ To increase a motor vehicle, the invention also reverses the transmission vibration

i 5 task is based on a generic oscillation an undesired further shift of the KoI-

Yi supply damper, especially for use with Kraftbens with decreasing displacement forces

p5 vehicles to create the jumping out of the one The invention is in the following for example an-

Sv laid Ganges prevented without the necessary hand of the drawing described; in this shows

Ο the switching forces can be increased. 20 Fig. 1 is a schematic view of a device on a

S) This object is achieved according to the invention by the shift linkage arranged with a drive block

; 'Characteristic features of claim 1- vibration damper,

i solves. F i g. 2 is a partially sectioned side view of the

The preload of the shooting body in its resting vibration damper when the valve is open,

position by means of a magnet causes the ball 25 F i g. 3 the same view as FIG. 2, but with

remains in its rest position until the valve on its closed,

;,. attacking back pressure has reached the value at which F i g. 4 shows a section essentially along line IV-IV

i should close the valve. This value should expediently be shown in FIG. 2,

i- be about twice as high as the value which, in FIG. 5, is an enlarged section from FIG

'; fast, sporty shifting is achieved. The past 30 better illustration of the valve,

P correct flow velocity is therefore expedient. 6 shows a section essentially along line X-X

i? usually the one who is at the risk of a gangster in F i g. 5,

:; jumping out causing strong vibrations F i g. 7 shows a section essentially along line VII-

:: 'or shaking movements of the transmission occurs, while VII in F i g. 5 and

p rend in the 35 F i g. 8 is a further embodiment of the when

The valve used in the valve used in a partial flow rate of the closing body vibration damper

E? has not yet moved out of its rest position, side view in section, analogous to FIG. 5.

Depending on the change in the displacement of the piston, the various figures in the drawing show a

ί7 term forces occur suddenly, so that for other corresponding components with the same reference time

|| slow as well as medium displacement speeds.

i |! plunger not a fig due to the valve. 1 shows schematically a gearshift lever 30 ra increase in piston resistance is noticeable on a motor vehicle, which via a shift linkage 31 ψ on the other hand, the valve remains closed until it is connected to the transmission block 32 of the vehicle tM pushes the closing body into its valve seat Between a load pressure attached to the gear block 32 has completely disappeared, so that a subsequent 45 gerblock 35 and a displacement of the piston arranged on the shift linkage 31 as a result of the already mentioned bearing block 34 extends a vibration; '■' of the decreasing forces is excluded. dampers 33 are substantially parallel to Schaltgestän- 'An advantageous further development of the invention provides ge 31, which at switching movements of the Schaltgesich characterized in that the valve has two stänges in the flow direction 31 corresponding shortened or lengthened and''J consecutively spaced closing body 50 vibrations between the shift linkage 31 and; has, which attenuates with on the opposite to the gear block 32 so that a jump-out side or provided between them valve seats cooperate gene a gear by swinging in opposite directions. In this way, it is possible to prevent the closing body and valve seats of the shift linkage 31 and the gear block 32 from being impacted. According to FIG. 1 is the vibration damper lowing pretensioning forces either the same or 55 by means of a fastening element arranged on the cylinder base in order to optimize the arrangement for transmission connection piece 36 or by means of a piston rod for a specific application. ge 37 via universal joints 58 and 59 to the bearing - In the aforementioned embodiment, it is expediently attached to blocks 34 and 35, respectively, in order to be essentially vertical when they occur on the mutually facing or perpendicular to the extension of the shift linkage 31 - L facing away from each other sides of the closing body to be able to record the 50 de movements.

Closing body until the critical baffle is reached. The vibration damper 33 points to FIG. 2 one

force in the open position, a flow open on one side cylinder 26 with an axially

Path-leaving magnets are provided. As a result, the piston 24 can be pushed on, the piston rod of which is located

can the desired sudden response of the through the bottom 38 of the cylinder 26 in the direction of the

Vibration damper when the critical 65 transmission block 32 or the shift linkage 31 is exceeded

Stowage force are further favored. stretches. The piston rod 37 is through an opening 39

Although the one in the floor 38 connecting the two work spaces is passed through tightly.

Channel can be arranged in the piston, it is at a The opposite end of the cylinder 26 is through

5 6

a cover 60 closed, on which the fastening- The vibration damper 33 described works

Connection piece 36 for attachment to the gearbox as follows:

beblock 32 or on the shift linkage 31 is the piston 24 as a result of a switching process with

As in Fig. 2, 3, the piston 24 is through at a conventional slow to medium speed

Way without any bores relatively thinly moved out of the cylinder 26, the hydraulic fluid flows

In addition to the cylinder 26, a pipe 15 is formed parallel to it from a working space via the channel 11 'and

Channel 11 'arranged in the cylinder housing 10, which the opened valve 12 into the other working space,

for manufacturing reasons, the same length as the closing body 13, 13 'from the permanent magnet

Cylinder 26 is and via bores 43 and 44 with the 1: en 18 and the permanent magnets 18,18 'in the out

Working spaces on both sides of the piston 24 in Stream io the F i g. 2, 5 and 8 visible opening positions

The channel 11 'is at its two ends, so that the hydraulic fluid can flow through

the end faces at the level of the cylinder base 38 or the practically no or only a very low resistance

The cylinder cover 60 is closed by a plug 45. is opposed.

In the axial channel 11 'between the bores, however, the piston 24 becomes as a result of gear jumping

43 and 44 a valve 12 fittingly and firmly arranged, the 15 generating vibrations quickly in the cylinder 26

a valve body 17, 17 'with valve seats 14, 14' pushed around, so that the flow velocity a

grips, exceeds a predetermined value formed in the form of balls closing, so is by the depending

body 13,13 'are used (see also Fi g. 5 to 8). according to the direction of flow on one of the closing bodies

Between the two closing bodies 13, 13 ', a dynamic pressure acting as a per- 113, 13' is the holding force of the magnetic

Manentmagnet 18 provided, which overcomes the closing body 13, 20 en 18, and the corresponding closing body

13 'holds in its rest position in which it holds one by 13, 13' on the associated valve seat 14,

Have a distance to the valve seats 14,14 '. 114 'sealingly. At this moment the hydraulic

The valve body 17, 17 'has a continuous fluid flow velocity abruptly on the channel, which is reduced to zero from inlet bores 40, 40' so that the dynamic pressure also disappears at both ends of the valve body 17, 17 'and the closing one in its closed position Closing body 13, 13 'can then be released when reversing the ordered flow passages 42. Between the direction of movement in the course of the oscillation silk flow passages 42 are located in the peripheral closed position and come back in the direction of the closing body 13, 13 'axially connecting abutment on the magnet 18, where it is held.
Crosspieces 17 ", which serve as closing bodies 13, 13 '- 30 Now comes the gear oscillation in the radial direction with one of the balls, so that they only move in the opposite direction relative to the valve channel or to the channel 11' axial loading - Half-period, so the damper force acting in the opposite direction will be able to execute the other closing body

According to FIG. 5 is located between the soft magnets 113, 13 'on its associated valve seat 14' and 14 respectively

table-designed closing bodies 13, 13 'brought a permanent 35 system, whereby the valve 12 in opposite

nentmagnet 18, the from F i g. 6 apparent flat set direction closes the closing-opening game

Has cross-section to next to it further flow around it can now be repeated in the opposite direction.

tion channels 42 for the unimpeded passage of the moves so the gear block 32 or the KoI-

To leave hydraulic fluid. rod 37 in FIG. 1.2 to the left, the Cber-

As indicated in FIGS. 2 to 4, the closing body must step above 40 of the critical dynamic pressure

the hydraulic fluid 15 an air cushion 46 at 13 'is moved to the right into its closed position, while

be provided to the vibration damper so that when the gear block 32 or

sen damping properties, so that the closing body 13 to the piston rod 37 to the right

abrupt braking in the case of a closure that executes a closing movement to the left.

Valve 12 can be avoided and the different 45 shifting of the shift linkage 31 compared to the gear

Piston rod volume with retracted and extended drive block 32, which would cause gear jumping.

Piston rod 37 is balanced. de, is thus reliably prevented

In the F i g. 2 and 3 are the two extreme positions

of the piston 24 once in full lines and 3 sheets of drawings

on the other hand illustrated in dashed lines in FIG. 50
F i g. 8 shows a second valve 12 whose valve seats 14, 14 'in the middle of the valve body 17, 17'
arranged and through a connecting bore 42 '
are connected. The closing bodies 13, 13 'forming

Balls come from opposite sides at 55
corresponding ram pressure to the seats
14, 14 'and detach themselves from permanent magnets 18, 18' which are arranged on opposite sides of the valve seats 14, 14 'and which have a similar cross-section

as with the valve according to Fig. 5 are designed to 60
to allow the hydraulic fluid to flow through laterally. In principle, the valve 12 works according to FIG. 8th
just like that according to FIG. 5.

Although the valve 12 according to FIG. 5 in the described vibration damper 33 in addition to the cylinder 65
26 provided channel 11 'is arranged it could
also be arranged in the piston 24, this then
should be made sufficiently thick.

Claims (4)

1 2 already known, vibration damper with in a Zy patent claims: to use linder arranged pistons, due to their structure and their damping characteristics 1. Vibration damper, in particular between the shift linkage, force the transmission movements see the transmission block and the shift linkage 5 to follow. A hard damper is e.g. B. a relative of a motor vehicle and arranged parallel to the rigid connection between the transmission and the Ge shift linkage is switched, with a hydraulic rod and prevents gear jumping almost completely, Liquid-filled, at its bottom with one but has the disadvantage that when switching, where yes one Fastening connector provided cylinder and relative movement between gear and linkage a piston that must follow the cylinder in two through io, higher forces are to be applied to the dividing a duct connected working spaces and shortening or lengthening the damper. At a is attached to a piston rod, the conditions are just reversed by a very soft damper The cylinder-closing lid is turned tightly, d. H. there is hardly any danger of gear jumping is carried out and reduced at its outwardly protruding, but the switching forces are only little End has a fastening connector, with 15 raised in which the working spaces of the cylinder connect- So with known vibration dampers you have to dsn channel one of two valve seats and at least always a compromise between the smallest possible one of the valve seats away into an open position holding switching forces and the most complete possible pre-tensioned closing body existing gene avoiding gear jumping find what last valve is arranged that the borrowed at a shift 20 leads to the fact that the switching forces are greater than inheritance of the piston in the cylinder are desired to flow through it and nevertheless a gear hydraulic fluid every now and then in the open state only one jump occurs opposed low resistance and the case of a generic, known Schwin-closer body against the biasing force of the supply damper (DE-OS 20 33 530) is in a hydraulic fluid with oil is so circulated that above-25 filled cylinder a piston is arranged, the one half a predetermined continuous drilling force that runs counter to the preload allele to the piston rod and is directed by rapid piston movement, in which a ball is received. The conditional flow velocity of the hydraulic fluid flowing through the bore hole is partially covered at its axial ends through a hole each on the valve, so that the ball together-closing body due to the corresponding increase in dynamic pressure with the holes in the perforated disc forms a valve The damming force between the ball and the perforated disks is so great that it overcomes the pre-tensioning force, there are springs that pre-tension the ball in its open position, characterized in that it is generated in the axial center of the piston,
At least one magnet (18, 18 ') fixed relative to the valve body (17, 17') in front of the pre-tensioning force, the oil will see the ball open from the springs and the closing body (13, 13 ') held magnetically, so that the piston displacement is practically designed and is not hindered. When moving very quickly 2. Vibration damper according to claim 1, that the piston in the oil-filled cylinder is characterized by the fact that the valve (12) two dynamic pressure acting in a ball is so great that the pre-flow direction one behind the other at a distance of 40 clamping force the springs is overcome and the orderly closing body (13, 13 ') has, which ball vermit the corresponding hole in the perforated disc on the sides facing away from each other or closes. Further displacement of the piston is then practically impossible between the valve seats (14, 14 ') provided between them.
cooperate. However, if the piston with a medium 3. Vibration damper according to claim 2, shifted 45 speed in the cylinder, so causes the characterized in that the dynamic pressure acting on the ball against each other pulls against the force turned or facing away from each other sides of one of the springs already a displacement of the ball, Closing body (13,13 ') the closing body (13,13') until whereby the oil flow through the piston is already in Reaching the critical damming force in the open is restricted, so that a shift of the Kolposition holding a flow path free 50 bens an increased resistance is opposed. Magnets (18,18 ') are provided. If such a vibration damper, which for 4. Vibration damper according to one of the claims washing machines was developed in a Kraftche 1 to 3, characterized in that the by-vehicle transmission uses the so-called there To prevent the duct (H ') connecting the work spaces in the cylinder gear jumping, it is set at the switchover housing is arranged. 55 th of the individual gears, there is an undesirably high resistance to the shifting process, which is is lower than with a vibration damper without a valve, as described for example in DE-OS 30 06 296, but this resistance also hinders one The invention relates to a vibration damper 60 fast switching process, as it is particularly in Kritinach the preamble of claim 1. see driving situations may be necessary. It is already known that in the case of strong shaking movements, DE-OS 27 45 768 describes a hydraulic system the vehicle transmission in the direction of travel the shock absorber with a arranged in a cylinder Shift linkage due to its inertia known as this moving piston, the piston separating the cylinder in two not always go in the same direction, share 65 workspaces. The two separated from the piston so it can happen that the activated working spaces of the cylinder are over in the cylinder counter pop out by itself while driving. This housing arranged lines connected to each other, The process is called gait jumping. It is now in which a valve is placed between two