CS209089B1

CS209089B1 - Telescopic elastic element

Info

Publication number: CS209089B1
Application number: CS778579A
Authority: CS
Inventors: Jiri Bednar
Original assignee: Jiri Bednar
Priority date: 1979-11-14
Filing date: 1979-11-14
Publication date: 1981-10-30

Description

(54) Teleskopický pružiaci element(54) Telescopic spring element

Vynález sa týká teleskopického pružiaceho elementu, ktorý je vhodný pre odpruženie kolies motorových vozidiel.The invention relates to a telescopic spring element suitable for the suspension of motor vehicle wheels.

Kvalitně odpruženie kolies motorových vozidiel je okrem dalších faktorov podmienené predovšetkým priebehom charakteristiky závislosti zaťaženia pružiaceho elementu na jeho zdvihu a tlmením kmitania kolesa voči podvozku vozidla. Zo známých převedení pružiacich elementov požiadavkám na priebeh charakteristiky najlepšie a najjednoduchším spósobom vyhovuje riešenie, kde v rúrke do ktorej sa pri preperovaní zasúva klzák, je stláčaná valcovná pružina vzopieraná medzi operku rúrky a čelo klzáku a vo vnútri tejto pružiny je umiestnená pomocná pružina uchytená na čele klzáku a na tiahlo volné prechádzajúce otvorom operky rúrky. Tiahlo je na koncoch opatřené osadeniami, ktoré spolu s pružnými dorazmi umiestnenými medzi operku rúrky a osadenia tiahla obmedzujú pohyb tiahla voči operke rúrky. Tým možno dosiahnuť strmého nárastu charakteristiky zaťazenia v závislosti na zdvihu v krajných oblastiach zdvihu a pozvolného nárastu charakteristiky v strednej časti zdvihu, kedy tiahlo νοΓηβ prechádza operkou. Zlomy priebehu charakteristiky sú plynulo napojené pružnými dorazmi. Nevýhodou tohto riešenia je obťažné zabudovanie hydraulického tlmenia na ktoré nemožno využiť priestor pružiaceho elementu a tlmeme musí byť převedené osobitným zariadením, tiahlo pomocnej pružiny ktoré je s ohladom na pevnostně požiadavky oceíové, je nedostatočne bočné vedené otvorom ocelověj operky rúrky v priestore, kde nemožno sporahlivo zabezpečit’ mazanie a v strednej oblasti zdvihu pri nezaťaženej pomocnej pružině je pohyb tiahla v otvore operky sprevádzaný nepříjemným hlukom.The quality of the suspension of motor vehicle wheels is, among other factors, conditioned mainly by the course of the characteristic of the load dependence of the spring element on its lift and the damping of the wheel oscillation in relation to the vehicle chassis. Of the known transversing of the spring elements, the best and simplest way of meeting the requirements is to provide a solution in which the tube into which the glider is inserted during washing is a compressed cylindrical spring supported between the tube support and the glider face and of the glider and the rod loosely passing through the opening of the pipe support. The rod is provided at the ends with pads which, together with the elastic stops placed between the pipe support and the rod pads, limit the movement of the rod with respect to the pipe support. Thereby, a steep increase in the load characteristic in relation to the stroke can be achieved in the extreme stroke regions and a gradual increase in the characteristic in the middle part of the stroke as the rod νοΓηβ passes through the support. The breaks in the characteristic curve are continuously connected by spring stops. The disadvantage of this solution is the difficult installation of hydraulic damping to which the space of the spring element cannot be used and the damping must be transferred by a special device, the auxiliary spring rod being steel side is insufficiently laterally guided through the opening of the steel pipe support. lubrication, and in the middle stroke region with the unloaded auxiliary spring, the movement of the rod in the opening of the backrest is accompanied by unpleasant noise.

Tieto nevýhody odstraňuje teleskopický pružiaci element podlá vynálezu podstata ktorého je v tom, že pružina je zavesená jednak na závesnom oku piestnice a jednak na presuvníku tvaru prstenca axiálně volné vedeného vylahčením vodiaceho telesa, ktoré je plášťom spojené so závesom. Medzi presuvníkom a dorazovou plochou vodiaceho telesa je umiestnený přechodový doraz, medzi presuvníkom a osadením vodiaceho telesa je umiestnený spatný doraz, keď vyrahčenie vodiaceho telesa je ukončené jednak dorazovou plochou a jednak osadením, tlačná pružina je opretá o presuvník a závěs.These drawbacks are overcome by the telescopic spring element according to the invention, in which the spring is hinged on the piston rod hinge and on the ring-shaped shifter axially loosely guided by lightening the guide body which is connected to the hinge by the housing. A transition stop is located between the slider and the guide body stop surface, a wrong stop is located between the slider and the guide body shoulder when the guide body ejection is terminated by both the stop surface and shoulder, the compression spring is supported on the slider and hinge.

Výhody teleskopického pružiaceho elementu podTa vynálezu sú v tom, že pri vyhovení požiadavkám na priebeh charakteristiky závislosti zaťaženia na zdvihu teleskopického pružiaceho elementu jednoduchými a technologicky nenáročnými prostriedkami, sú vzájomné pohyblivé členy kvalitně vedené a výhodné namáhané, takže sú na ich výrobu použitelné materiály ktoré sú i pri vzájomnom pohybe za nedostatočného přívodu maziva nehlučné, sú vytvořené předpoklady pre jednoduché zabudovanie hydraulického tlmenia umiestnením škrtiaceho orgánu do piestnice.Advantages of the telescopic spring element according to the invention are that in meeting the requirements of the course of the characteristic of the load dependence on the lift of the telescopic spring element by simple and technologically undemanding means, the mutually movable members are well guided and advantageously stressed so that When moving relative to one another with insufficient lubricant supply, there are conditions for easy incorporation of hydraulic damping by placing the throttle in the piston rod.

Příklad prevedenia teleskopického pružiaceho elementu podía vynálezu je znázorněný na připojených obrázkoch 1 a 2, kde obr. 1 představuje pozdížny rez, obr. 2 priečny rez v mieste presuvníka, na obr. 3 je znázorněná charakteristika závislosti zaťaženia na zdvihu teleskopického pružiaceho elementu podía vynálezu.An example of an embodiment of a telescopic spring element according to the invention is shown in the attached Figures 1 and 2, wherein FIG. 1 is a longitudinal section, FIG. 2 is a cross-sectional view of the shifter; FIG. 3 shows a characteristic of the load versus lift of the telescopic spring element according to the invention.

Piestniea 1, prichytená k závěsnému oku 4, je vedená v závese 2 a v jeho vodiacom telese 5, ktoré sú spolu spojené plášťom 3. Pružina 12 je prichytená jednak na závesnom oku 4 piestnice 1 a jednak na presuvníku 8 tvaru prstenca axiálně volné vedenom vyíahčením 6 vodiaceho telesa 5. Medzi presuvníkom 8 a dorazovou plochou 16 vodiaceho telesa 5 je umiestnený přechodový doraz 11. Medzi presuvníkom 8 a osadením 9 vodiaceho telesa 5 je umiestnený spátný doraz 15. Vyíahčenie 6 je ukončené jednak dorazovou plochou 16 a jednak osadením 9. Tlačná pružina 13 je vzopieraná medzi presuvník 8 a závěs 2. V piestnici 1, ktorá je tvořená ocelovou rúrkou, je zabudovaný škrtiaci orgán 7 hydraulického tlmenia, ktorý v závislosti na rýchlosti vzájomného pohybu piestnice 1 a závěsu 2 škrtí prietok tlmiacej kvapaliny medzi dutinou 17 závěsu 2 a medzi obvodovou dutinou 10 vytvořenou medzi plášťom 3 a piestnicou 1, keď dutina 17 a obvodová dutina 10 sú přepojené otvorom 18 piestnice 1 a vnútorným objemom 19 piestnice 1. Medzi osadením 9 a závěsným okom 4 je umiestnený doraz 14. V bode A pri nulovom stlačení h a nulovom zatažení F je pružina 12 nezaťažená, tlačná pružina 13 je stlačená a jej predpátím stláča presuvník 8 zpátný doraz 15 na osadenie 9. Pri odskočení kolesa pri zápornom zdvihu h je záporné zaťaženie F absorbované tahovým namáháním pružiny 12, pri stláčaní z bodu A smerom k bodu B narastá zaťaženie F a zdvih h pri stláčaní pružiny 12, ktoré je blízko boduThe piston rod 1, attached to the hinge eye 4, is guided in the hinge 2 and in its guide body 5, which are connected together by the housing 3. The spring 12 is attached both to the hinge eye 4 of the piston rod 1 and There is a transition stop 11 between the slider 8 and the stop surface 16 of the guide body 5. Between the slider 8 and the shoulder 9 of the guide body 5, a return stop 15 is provided. 13 is restrained between the slider 8 and the hinge 2. In the piston rod 1, which is formed by a steel tube, is a throttling member 7 of hydraulic damping which, depending on the speed of mutual movement of the piston rod 1 and hinge 2 throttles the flow of buffer. between the peripheral cavity 10 formed between the housing 3 and the piston rod 1 when the cavity 17 and the peripheral du 10 are interconnected by the piston rod opening 18 and the piston rod internal volume 19. A stop 14 is placed between the shoulder 9 and the eyelet 4. At point A at zero compression and zero retraction F, the spring 12 is unloaded, the compression spring 13 is compressed and biased. When the wheel bounces at a negative stroke h, the negative load F is absorbed by the tensile load of the spring 12, when compressed from point A towards point B, the load F and the stroke h when compressing the spring 12 close to point

Claims

209089, which is advantageous and advantageously stressed, so that materials which are lubricant-free, even in mutual movement with insufficient feed, are suitable for their manufacture, and the prerequisites for simple incorporation of the hydraulic damping by placing the throttle into the piston rod are provided. An example of an embodiment of a telescopic spring element according to the invention is shown in the accompanying Figures 1 and 2, wherein Fig. 1 is a cross-sectional view, Figs.

2 is a cross-sectional view of the transfer point; FIG.

3 shows the load dependency characteristic of a telescopic spring element according to the invention. The piston 1, attached to the hinge eye 4, is provided in the hinge 2 and in its guide body 5, which are connected to each other by a sheath 3. The spring 12 is fixed on the hinge eye 4 of the piston rod 1 and on the other hand on the slider 8 in the form of an annular axial guide 6. a transverse stop 11 is provided by the transversal slide 8 and the stop surface 16 of the guide 5, a bad stop 15 is disposed on the intermediate slide 8 and the shoulder 9 of the guide body 5. The discharge 6 is terminated by the stop surface 16 and the single-slide 9. The compression spring 13 is supported by the intermediate slide 8 and the hinge 2. In the piston rod 1 formed by the steel tube, a hydraulic damping throttle body 7 is incorporated which, depending on the speed of relative movement of the piston rod 1 and the suspension 2, throttles the damping fluid flow between the hinge cavity 17 and the peripheral cavity 10 formed between the shell 3 and the piston rod 1. when cavity 17 and circumferential cavity 10 are overvoltage A stop 14 is disposed between the shoulder 9 and the hinge eye 4. At point A at zero pressure h and zero retraction F, the spring 12 is unloaded, the compression spring 13 is compressed and its biasing presses the slide 8 backward stop 15 into position 9. When the wheel is biased with negative lift h, the negative load F is absorbed by the stress of the spring 12, the load F and the lift when the spring 12, which is close to the object point, increases when pressed from point A to point B The telescopic spring element, which contains two different springs and at least two resilient spring stops which continuously vary the variations in the course of the telescopic spring element during variations in the use of the function of the two springs as a function of the stroke of the telescopic spring element, characterized in that the spring (12) is attached to the hinge eye (4) of the piston rod (1) ) and the shifter (8) t boiling of the ring, axially loosened by the ejection (6) of the guide body (5), A engaged by the biasing of the compression spring 13. By increasing the load F near the point B of the spring 12, the prestressing of the compression spring 13 is approached to such an extent that the resiliency of the poor stop 15 is exhibited. the increasing movement of the slide 8 in the direction of compression of the hinge 4 until the pre-loading is in point B, as compared to the state in point A due to the return of the backstop 15 of the compressed compression spring 13, in equilibrium with the transmitted spring 12. Between the point B-D the spring 12 is shared by the spring 12 i the compression spring 13 connected in series with the movement of the slide 8 is relatively slower to the movement of the path 1 in the same sense, thus increasing the load F between the points B-D is more gradual than the intermediate points A-B. At point D, the shifter 8 of the abutment stop 11 and the further increase of the stroke h towards the point F is a portion of the load increase F engaged by the transition abutment 11 to the abutment surface 16 of the guiding body 5, until the elastic stop 11 is virtually negligible and near the point of contact. D between the points -D-E, the stroke transfer device 8 is no longer moved and the load increase F is then captured up to the point of insertion E only of the spring 12, thus the characteristic curve between D-E is steeper than between point B-D. From point E to the maximum stroke max, 14 is also present at the load rise F, which absorbs extremely high impacts, causing greater unevenness. The stop 13, the stop 11 and the stop 14 are made of a resilient material shaped so as to deflect continuously connected to the load F as a function of the stroke h of the points B, D, E. The static load on the vehicle corresponds to point C, where the free load F on the stroke h is loose, so the suspension responds sensitively to the smaller inequalities of the truck. The energy generated by the passage through the high-velocity is absorbed by the steep increase in the characteristic in the D-hmax region, the energy of the bouncing wheel is absorbed by the course B-A and further in the negative stroke h by the negative load F. THE INVENTION which is the jacket (3) associated with the hinge (2), wherein a transition stop (11) is disposed between the shifter (8) and the abutment surface (16) of the guide body (5), and a dead stop (15) is arranged between the shifter (8) and the shoulder (9) of the guide body (5). ) when the ejection (6) is terminated by a stop surface (16) and by a shoulder (9) and the compression spring (13) is supported on the pusher (8) and the hinge (2). 3 drawings