DK149990B - HYDRAULIC STEERING DEVICE, ISAES FOR VEHICLES - Google Patents
HYDRAULIC STEERING DEVICE, ISAES FOR VEHICLES Download PDFInfo
- Publication number
- DK149990B DK149990B DK480980AA DK480980A DK149990B DK 149990 B DK149990 B DK 149990B DK 480980A A DK480980A A DK 480980AA DK 480980 A DK480980 A DK 480980A DK 149990 B DK149990 B DK 149990B
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- Denmark
- Prior art keywords
- control
- pressure
- valve
- connection
- pressure chamber
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- 230000007935 neutral effect Effects 0.000 claims description 11
- 230000004323 axial length Effects 0.000 claims description 3
- 239000012530 fluid Substances 0.000 description 9
- 238000006073 displacement reaction Methods 0.000 description 7
- 230000007423 decrease Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- 238000011017 operating method Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
- B62D5/09—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by means for actuating valves
- B62D5/093—Telemotor driven by steering wheel movement
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
- Power Steering Mechanism (AREA)
Description
149990149990
Opfindelsen angår en hydraulisk styreanordning, især for køretøjer, med en styreventilanordning, som over en første og en anden arbejdstilslutning er forbundet med hver et trykrum i en stempel-cylinder-anordning og over en tanktilslutning 5 med en tank samt har en ventilglider, som er belastet af neutralstillingsfjedre og for enden af trykket i to styre-trykrum, som hver er forbundet med en tilslutning til en af et manuelt aktiveringsorgan indstillelig styrepumpe og over en kontraventilanordning er forbundet med en hovedpumpe.BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to a hydraulic control device, in particular for vehicles, with a control valve device which is connected, over a first and a second working connection, to each a pressure chamber in a piston-cylinder device and over a tank connection 5 with a tank and has a valve slider which is loaded by neutral position springs and at the end of the pressure in two control pressure chambers, each connected by a connection to a control pump adjustable by a manual actuator and over a check valve device by a main pump.
10 Ved en kendt styreanordning af denne art (FR-PS 1 465 422, fig. 4) har ventilglideren to fremspring, som lukker de to arbejdstilslutninger i neutralstillingen og ved en forskydning altid forbinder den ene arbejdstilslutning med et sty-retrykrum og den anden arbejdstilslutning med tanktilslut-15 ningen. Hovedpumpen er direkte forbundet med begge styre-trykrum over hver sin kontraventil og i neutralstillingen over en kortslutningsvej med tanktilslutningen. Ved en omstilling af det manuelle aktiveringsorgan ændres trykket i de to styretrykrum, således at ventilglideren forskydes fra 20 sin neutralstilling. Der strømmer da trykmiddel fra hovedpumpen over en kontraventil, styrepumpen og et styretrykrum ind i stempel-cylinder-anordningens ene trykrum, mens det andet trykrum er forbundet med tanken. Stempel-cylinder-anordningens to trykrum har lige store aktive flader. Det er 25 herved uheldigt, at det manuelle aktiveringsorgan først skal tilbagelægge en vis dødvej, inden stempel-cylinder-anordnin-gen kan bevæges, fordi ventilglideren først skal forskydes et vist stykke, inden den ene arbejdstilslutning kan forsynes med trykvæske.10 In a known control device of this kind (FR-PS 1 465 422, Fig. 4), the valve slider has two projections which close the two working connections in the neutral position and, at one displacement, always connect one working connection to a control room and the other working connection. with the tank connection. The main pump is directly connected to both control pressure compartments above each check valve and in the neutral position over a short circuit path with the tank connection. By changing the manual actuator, the pressure in the two control pressures is changed so that the valve slider is displaced from its neutral position. Pressure medium then flows from the main pump over a check valve, the control pump and a control pressure chamber into one pressure chamber of the piston-cylinder device, while the other pressure space is connected to the tank. The two pressure chamber of the piston-cylinder device has equal active surfaces. It is thus unfortunate that the manual actuator first has to cover a certain dead path before the piston-cylinder device can be moved, because the valve slide must first be displaced a certain distance before one working connection can be supplied with pressure fluid.
30 Endvidere kendes en pneumatisk drosselforstærker (DE-PSFurther, a pneumatic choke amplifier (DE-PS
21 16 197), ved hvilken der ved hjælp af et dobbelt ventillegeme, som af et styretryk kan forskydes mod kraften af en fjeder, dannes to modsat indstillelige drosler, som er anbragt mellem en lufttilførsels-tilslutning og en med atmos 2 149990 færen forbundet tilslutning. Dette giver en trykdeler, således at der mellem de to drosler kan aftages et af styretrykket afhængigt udgangstryk. Som anvendelsesområder er angivet pneumatiske styresystemer og computere.21 16 197), by means of which a double valve body, which can be displaced by a control pressure against the force of a spring, creates two opposable adjustable thrusts which are arranged between an air supply connection and a connection connected to the atmosphere. . This provides a pressure divider so that an output pressure dependent on the control pressure can be reduced between the two thrusters. Fields of application are pneumatic control systems and computers.
5 Således er en hydraulisk styreanordning kendt (AT-PSThus, a hydraulic control device is known (AT-PS
306 473), ved hvilken der er anvendt en stempel-cylinder-an-ordning med differentialstempel. Til styreventilanordningen hører en membran, hvis uden for en indspænding anbragte kant inddeler et ringrum i to styretrykrum, i hvilke der ved 10 hjælp af en forstyringsanordning kan frembringes forskellige tryk. Membranens midterste del danner sammen med to udstrømningsåbninger to modsat indstillelige drosler, af hvilke den ene forbinder trykrummet med den mindste aktive flade af stempel-cylinder-anordningen med det andet trykrum, og den 15 anden drossel forbinder det sidstnævnte trykrum med tanken.306 473) using a differential cylinder piston-cylinder device. The control valve assembly includes a diaphragm whose outer edge of a clamp divides an annulus into two control pressure chambers in which different pressures can be generated by means of a control device. The middle part of the diaphragm together with two outflow openings form two opposable throttles, one of which connects the pressure chamber with the smallest active surface of the piston-cylinder device to the other pressure chamber and the other choke connects the latter pressure chamber to the tank.
Arbejdstrykket tilføres direkte det førstnævnte trykrum.The working pressure is directly applied to the former pressure chamber.
Herved har man brug for en forholdsvis stor energi i forstyringskredsen for at opnå en sikker indstilling af membranen.This requires a relatively large amount of energy in the disturbance circuit to obtain a safe setting of the membrane.
En ved styreindretninger ønsket tilbagevirkning af de stem-20 plet belastende ydre kræfter til forstyringsanordningen er ikke mulig.A return desired by the control means of the piston-loading external forces to the control device is not possible.
Formålet med opfindelsen er at angive en hydraulisk styreanordning af den i indledningen beskrevne art, ved hvilken en indstilling af det manuelle aktiveringsorgan straks bevirker 25 en indstilling af stempel-cylinder-anordningen, dvs. at der ikke er nogen død zone i neutralstillingsområdet.The object of the invention is to provide a hydraulic control device of the kind described in the preamble, in which an adjustment of the manual actuator immediately causes an adjustment of the piston-cylinder device, ie. that there is no dead zone in the neutral position area.
Denne opgave løses ifølge opfindelsen ved, at stempel-cylinder-anordningen har et differentialstempel, at den til trykrummet med den mindste aktive flade førende første arbejds-30 tilslutning permanent er forbundet med det første styretrykrum og er adskilt fra tanktilslutningen, og at der forefindes to af ventilglideren modsat indstillelige drosler, af hvilke den ene drossel forbinder det andet styretrykrum med 3 149990 den anden arbejdstilslutning, og den anden drossel forbinder den anden arbejdstilslutning med tanktilslutningen.This task is solved according to the invention in that the piston-cylinder device has a differential piston, that it is permanently connected to the first control pressure chamber for the pressure chamber with the least active flat leading-first connection and is separated from the tank connection, and that two adjustable throttles of the valve slider, of which one throttle connects the other control pressure chamber to the other working connection, and the other throttle connects the other working connection to the tank connection.
Ved denne konstruktion danner de to modsat indstillelige drosler en trykdeler. Det mellem de to drosler aftagne tryk 5 danner i stempel-cylinder-anordningens trykrum med den største aktive flade en kraft, som sammenlignes med en kraft, der dannes ved hjælp af det ikke reducerede tryk i trykrummet med den mindste aktive flade. Ved hjælp af den af det manuelle aktiveringsorgan indstillelige styrepumpe fremkom-10 mer der trykforskelle i de to styretrykrum, hvorved ventilglideren forskydes. Denne forskydning fører straks til en trykændring mellem de to drosler og dermed til en forskydning af stemplet i den ene eller den anden retning. En yderligere fordel ligger i, at ydre kræfter, som virker på stem-15 plet, fører til en forskydning af ventilglideren således, at den ydre kraft kompenseres ved hydrauliske kræfter. Desuden er forekomsten af denne ydre kraft over styrepumpen mærkbar på det manuelle aktiveringsorgan, således at der også kan modstyres med hånden.In this construction, the two oppositely adjustable thrusters form a pressure divider. The pressure 5 between the two thrusters forms in the pressure chamber of the piston-cylinder device with the largest active surface a force which is compared with a force generated by the non-reduced pressure in the pressure chamber with the smallest active surface. By means of the control pump adjustable by the manual actuator, pressure differences are obtained in the two control pressure chambers, whereby the valve slider is displaced. This displacement immediately leads to a pressure change between the two thrusters and thus to a displacement of the piston in one or the other direction. A further advantage lies in the fact that external forces acting on the piston lead to a displacement of the valve slider such that the external force is compensated by hydraulic forces. Furthermore, the presence of this external force over the control pump is noticeable on the manual actuator, so that it can also be controlled by hand.
20 Ved en særlig enkel udførelsesform er der sørget for, at en med den anden arbejdstilslutning forbundet ringnot i styre-ventilanordningens hus til dannelse af de to drosler samvirker med et fremspring på ventilglideren, som har en mindre aksial længde end ringnoten. Det er derfor tilstrækkeligt 25 med en meget enkelt udformet ventilglider i et meget enkelt udformet hus for at opnå det ønskede mål.In a particularly simple embodiment, a ring groove connected to the other working connection in the housing of the control valve device for forming the two thrusters is provided to cooperate with a projection on the valve slider having a smaller axial length than the ring groove. Therefore, a very simple valve valve slider in a very simply designed housing is sufficient to achieve the desired goal.
Det anbefales at anvende en trykreguleret hovedpumpe. Dermed er der sørget for, at der altid gås ud fra det samme trykniveau, hvilket letter dimensioneringen af de to drosler i 30 sammenligning med de aktive flader i de to trykrum i stem-pel-cylinder-anordningen.It is recommended to use a pressure regulated main pump. This ensures that the same pressure level is always assumed, which facilitates the sizing of the two thrusters in comparison with the active surfaces in the two pressure chambers of the piston-cylinder device.
Ved en foretrukken udførelsesform er der sørget for, at kon- 4 149990 traventilanordningen består af en enkelt kontraventil, og at hovedpumpen over kontraventilen er forbundet med det andet styretrykrum og parallelt med det andet styretrykrum over styrepumpen er forbundet med det første styretrykrum. Derved 5 opnås en enklere opbygning end ved den sædvanlige anvendelse af to kontraventiler, men det påvirker dog ikke funktionsmåden.In a preferred embodiment, the check valve assembly is made up of a single check valve and the main pump over the check valve is connected to the second control chamber and parallel to the second control room above the control pump is connected to the first control room. This makes 5 a simpler structure than the usual use of two non-return valves, but it does not affect the way it works.
Desuden kan kontraventilen være fjederbelastet. Dermed er det sikret, at selv ubetydelige svingninger i trykvæskesøj-10 len eller rystelser, som optræder ved et køretøj, ikke fører til fejlfunktioner.In addition, the non-return valve may be spring loaded. Thus, it is ensured that even insignificant oscillations in the pressure fluid column or vibrations occurring in a vehicle do not lead to malfunctions.
Fortrinsvis er begge styretrykrum over hver en hen imod dem åbnende kontraventil forbundet med tanken. Ved udfald af hovedpumpen tillader dette en nøddrift kun ved hjælp af styre-15 pumpen.Preferably, both control spaces above each of them are open to the tank with a non-return valve. In case of failure of the main pump, this allows emergency operation only by means of the control pump.
For nøddrift er det yderligere gunstigt, hvis styreventilan-ordningens tanktilslutning over en fjederbelastet, hen imod styreventilanordningen åbnende kontraventil er forbundet med tanken.For emergency operation, it is further advantageous if the tank valve arrangement of the tank valve over a spring-loaded check valve opening towards the control valve device is connected to the tank.
20 Opfindelsen forklares nærmere nedenstående ved hjælp af et på tegningen vist, foretrukket udførelseseksempel. Tegningen viser en hydraulisk styreanordning ifølge opfindelsen i diagram.The invention is further explained below by means of a preferred embodiment shown in the drawing. The drawing shows a hydraulic control device according to the invention in diagram.
En stempel-cylinder-anordning 1 har en cylinder 2 og et på 25 den ene side med en stempelstang 3 forbundet differential-stempel 4, som over et stangsystem 5 svinger et styrende hjul 6. I cylinderen findes der et første trykrum 7 med den mindste aktive flade F1 og et andet trykrum 8 med den største aktive flade F2.A piston-cylinder device 1 has a cylinder 2 and a differential piston 4 connected to a piston rod 3 on one side, which swings a steering wheel 6 over a rod system 5. In the cylinder there is a first pressure chamber 7 with the smallest active surface F1 and another pressure chamber 8 with the largest active surface F2.
30 En styreventilanordning 9 har et hus 10 med en boring 11 og 5 149990 en ventilglider 12. I huset befinder der sig en ringnot 13, som står i forbindelse med en første arbejdstilslutning 14, der fører til trykrummet 7. En anden ringnot 15 står i forbindelse med en anden arbejdstilslutning 16, som fører til 5 trykrummet 8. Yderligere findes der en tanktilslutning 17, som fører til tanken 18. Ved enderne er der anbragt to sty-retrykrum 19 og 20. I styretrykrummet 19 befinder der sig en neutralstillingsfjeder 21, som virker på en gennembrudt skive 22, Sidstnævnte understøttes enten på en aftrapning 23 i 10 huset eller på en endeflade af ventilglideren 12. i styretrykrummet 20 befinder der sig en neutralstillingsfjeder 24, som understøttes på en gennembrudt skive. Sidstnævnte ligger enten an med en aftrapning 26 i huset eller mod den anden endeflade af ventilglideren 12, Et første fremspring 27 på 15 ventilglideren 12 adskiller styretrykrummet 19 fra det med tanktilslutningen 17 forbundne rum. Med arbejdstilslutningen 16 danner et andet fremspring 28, som har en mindre aksial længde end ringnoten 15, to drosler 29 og 30, som ved en forskydning af ventilglideren 20 ændrer sig modsat i forhold 20 til hinanden.A control valve assembly 9 has a housing 10 with a bore 11 and 5 a slider 12. In the housing there is a ring groove 13 which communicates with a first working connection 14 leading to the pressure chamber 7. A second ring groove 15 is provided in connection with another working connection 16 leading to pressure chamber 8. Further, there is a tank connection 17 leading to the tank 18. At the ends there are arranged two control rooms 19 and 20. In the control room 19 there is a neutral position spring 21, acting on a pierced disc 22, the latter being supported either on a step 23 in the housing or on an end surface of the valve slide 12. In the control chamber 20 there is a neutral position spring 24 supported on a pierced disk. The latter abuts either a step 26 in the housing or against the second end surface of the valve slide 12. A first projection 27 of the valve slide 12 separates the control pressure chamber 19 from the space connected to the tank connection 17. With the working connection 16, a second projection 28, which has a smaller axial length than the ring groove 15, forms two thrusters 29 and 30 which, when displaced by the valve slider 20, change opposite to one another 20.
En styrepumpe 31 er indstillelig over et manuelt aktiveringsorgan 32. Styrepumpens 31 to sider er forbundet med tilslutningsledninger 33 og 34, som fører til styretrykrum-mene 19 og 20. Desuden er tilslutningsledningen 34 over en 25 fjederbelastet kontraventil 36 forbundet med tryksiden 37 af en hovedpumpe 38, som har en trykreguleringsanordning 39 til at holde udgangstrykket konstant. To sugeledninger 40, 40' med hver en kontraventil 41, 41' fører fra tilslutningsledningerne 33 og 34 til tanken 18. Tanktilslutningen 17 er 30 tilsluttet en kontraventil 42, som er belastet så stærkt af en fjeder, at ventilglideren 12 i nøddrift ved hjælp af det af styrepumpen 31 dannede tryk kan forskydes til venstre, uden at kontraventilen 42 åbner.A control pump 31 is adjustable over a manual actuator 32. The two sides of the control pump 31 are connected to connecting lines 33 and 34 which lead to the control chambers 19 and 20. In addition, the connection line 34 is connected via a spring-loaded check valve 36 to the pressure side 37 of a main pump. 38, which has a pressure control device 39 for holding the output pressure constant. Two suction lines 40, 40 ', each with a non-return valve 41, 41', lead from the connecting lines 33 and 34 to the tank 18. The tank connection 17 is connected to a non-return valve 42 which is so heavily loaded by a spring that the valve slider 12 in emergency operation by means of the pressure generated by the control pump 31 can be displaced to the left without the check valve 42 opening.
Med denne styreanordning fremkommer der følgende driftsmå-35 der: 6 149990 I den viste neutralstilling frembringer hovedpumpen 38 et tryk Pq . Trykket Pi i styretrykrummet 19 og trykket T?2 i styretrykrummet 20 er tilnærmelsesvis lig med Pg. Trykket Pi hersker også i trykrummet 7. I trykrummet 8 opstår derimod 5 et tryk P3, fordi der konstant over de to drosler 29 og 30 flyder en mindre trykmiddelstrøm, som bevirker en trykdeling på arbejdstilslutningen 16. Forholdet mellem drosselmodstandene i neutralstillingen er valgt således, at der i neutralstillingen gælder 10 Pi x F1 = P3 x F2With this control device, the following operating methods appear: 6 In the shown neutral position, the main pump 38 produces a pressure Pq. The pressure Pi in the control pressure chamber 19 and the pressure T 2 in the control pressure curve 20 are approximately equal to Pg. The pressure Pi also prevails in the pressure chamber 7. In the pressure chamber 8, on the other hand 5, a pressure P3 is created, because a constant flow of fluid over the two thrusters 29 and 30 causes a pressure distribution on the working connection 16. The ratio of the throttle resistors in the neutral position is thus chosen. that in the neutral position 10 Pi x F1 = P3 x F2
Som følge af denne kraftudligning bliver stemplet 4 stående.As a result of this force equalization, the piston 4 remains standing.
Ved en drejning af det manuelle aktiveringsorgan 32 til venstre stiger Pi ubetydeligt. Tilsvarende forskydes ventilglideren 12 til højre. Droslens 29 modstand stiger, mens dros-15 lens 30 modstand aftager. Som følge heraf falder det reducerede tryk P3. Stemplet 4 bevæges derfor til højre. Fra hovedpumpen 38 leveres trykvæske over kontraventilen 36, styrepumpen 31 og styretrykrummet 19 til trykrummet 7, mens trykvæske samtidigt kan ^strømme fra trykrummet 8 over dros-20 len 30 til tanken 18.By turning the manual actuator 32 to the left, Pi rises negligibly. Similarly, valve slider 12 is displaced to the right. The resistance of the throttle 29 increases while the resistance of the throttle 30 decreases. As a result, the reduced pressure P3 decreases. The piston 4 is therefore moved to the right. From the main pump 38, pressure fluid is supplied over the check valve 36, the control pump 31 and the control pressure chamber 19 to the pressure chamber 7, while the pressure fluid can simultaneously flow from the pressure space 8 over the throttle 30 to the tank 18.
Drejes det manuelle aktiveringsorgan 32 til højre, forskydes ventilglideren 12 til venstre. Som følge heraf stiger trykket P3 mellem droslerne 29 og 30. Stemplet 4 trykkes til venstre. Hetved strømmer der trykvæske fra hovedpumpen 38 25 over kontraventilen 36 og styretrykrummet 20 til trykrummet 8. Den samtidigt fra trykrummet 7 fortrængte trykvæske når over styrepumpen 31 ligeledes til trykrummet 8.If the manual actuator 32 is turned to the right, the valve slider 12 is shifted to the left. As a result, the pressure P3 increases between the thrusters 29 and 30. The piston 4 is pressed to the left. Pressure fluid flows from the main pump 38 25 over the check valve 36 and the control pressure chamber 20 to the pressure chamber 8. The pressure fluid displaced simultaneously from the pressure chamber 7 also reaches over the control pump 31 to the pressure chamber 8.
Hvis hovedpumpen 38 falder ud, kan en nøddrift opretholdes ved hjælp af styrepumpen 31. Skal stemplet 4 forskydes til 30 venstre, kan den yderligere nødvendige trykvæske leveres over sugeledningen 40', kontraventilen 41' samt styrepumpen 7 149990 31 til trykrummet 8. Ved en ønsket forskydning af stemplet 4 til højre kan den nødvendige trykvæske leveres over sugeledningen 40, kontraventilen 41 samt styrepumpen 31 til trykrummet 7, hvorved den fra trykrummet 8 afgivne væske kan 5 strømme over kontraventilen 42 til tanken 18.If the main pump 38 fails, an emergency operation can be maintained by the control pump 31. If the plunger 4 is moved to the left 30, the additional necessary pressure fluid can be delivered over the suction line 40 ', the check valve 41' and the control pump 7 to the pressure chamber 8. If a desired displacement of the plunger 4 to the right, the necessary pressure fluid can be supplied over the suction line 40, the check valve 41 and the control pump 31 to the pressure chamber 7, whereby the liquid delivered from the pressure space 8 can flow over the check valve 42 to the tank 18.
Hvis der på stemplet 4 virker en ydre kraft i pilens X retning, mens aktiveringsorganet 32 holdes fast, forskydes stemplet 4 ubetydeligt til venstre, hvorved ventilglideren 12 som følge af trykstigningen i styretrykrummet 19 bevæges 10 til højre. Herved forøges droslens 29 modstand, hvilket resulterer i en reduktion af trykket P3. Dette svarer til en kompensation af den udefra virkende kraft. Samtidig gør trykforøgelsen på P-j sig bemærket ved en tilsvarende impuls til styrepumpen 31, således at brugeren mærker et let slag 15 på aktiveringsorganet 32 og kan modstyre. Virker kraften imod pilens X retning, fremkommer der lignende forhold, dog således at ventilglideren 12 nu forskydes til venstre, og at trykket P3 forøges, og den ydre kraft på denne måde kompenseres.If on the piston 4 an external force acts in the direction of the arrow X while the actuator 32 is held in place, the piston 4 is shifted slightly to the left, whereby the valve slider 12 is moved 10 to the right due to the pressure increase in the control pressure chamber 19. This increases the resistance of the throttle 29 resulting in a reduction of the pressure P3. This corresponds to a compensation of the outside force. At the same time, the pressure increase on P-j is noticed by a corresponding impulse to the control pump 31, so that the user senses a slight blow 15 on the actuator 32 and can counter-act. If the force acts against the direction of the arrow X, similar conditions appear, however, so that the valve slide 12 is now displaced to the left and the pressure P3 is increased and the external force is thus compensated.
20 Hvis aktiveringsorganet 32 ikke fastholdes ved optræden af den ydre kraft, drejer det sig i forhold til stemplets 4 forskydning. Ved optræden af den ydre kraft er det dog også muligt at bremse stemplets forskydning ved at tilvejebringe et bremsemoment på det manuelle aktiveringsorgan 32. Hvis 25 den ydre kraft ikke er meget stor, kan man uden betænkning understøtte den heraf udløste indstilling af aktiveringsorganet.20 If the actuator 32 is not retained by the action of the external force, it is proportional to the displacement of the piston 4. However, upon occurrence of the external force, it is also possible to slow down the displacement of the piston by providing a braking torque on the manual actuator 32. If the external force is not very large, the adjustment of the actuating device triggered therefrom can be supported without consideration.
Hovedpumpens trykside 37 kan over en til kontraventilen 36 svarende yderligere kontraventil også forbindes direkte med 30 tilslutningsledningen 33. Desuden kan kontraventilerne 41, 41' herved også sammenfattes i en enkelt kontraventil, som kun shunter hovedpumpen 38, hvis man kan acceptere de kræfter, der er nødvendige for at åbne henholdsvis kontraventi U9990 8 len 36 og den tilsvarende yderligere kontraventil i nødsty-ringsdriften.The pressure side 37 of the main pump over a further non-return valve 36 corresponding to the non-return valve 36 can also be connected directly to the connecting line 33. In addition, the non-return valves 41, 41 'can hereby also be combined in a single non-return valve which shunts the main pump 38 only if one can accept the forces that are required to open the check valve U9990 8 36 and the corresponding additional check valve respectively in the emergency control operation.
Claims (3)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2946274 | 1979-11-16 | ||
| DE2946274A DE2946274C2 (en) | 1979-11-16 | 1979-11-16 | Hydraulic control device, in particular steering device |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| DK480980A DK480980A (en) | 1981-05-17 |
| DK149990B true DK149990B (en) | 1986-11-10 |
| DK149990C DK149990C (en) | 1987-10-12 |
Family
ID=6086142
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DK480980A DK149990C (en) | 1979-11-16 | 1980-11-12 | HYDRAULIC STEERING DEVICE, ISAES FOR VEHICLES |
Country Status (7)
| Country | Link |
|---|---|
| JP (1) | JPS5686206A (en) |
| DD (1) | DD154385A5 (en) |
| DE (1) | DE2946274C2 (en) |
| DK (1) | DK149990C (en) |
| FR (1) | FR2470883A1 (en) |
| GB (1) | GB2063192B (en) |
| IT (1) | IT1129859B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ATE18289T1 (en) * | 1981-09-14 | 1986-03-15 | Deere & Co | HYDRAULIC CONTROL DEVICE. |
| FR2540220A1 (en) * | 1983-02-01 | 1984-08-03 | Renault | HYDRAULIC CONTROL DEVICE, IN PARTICULAR POWER-ASSISTED STEERING |
| US4703819A (en) * | 1985-02-27 | 1987-11-03 | Nissan Motor Co., Ltd. | Full hydraulic power steering system |
| CN111452565A (en) * | 2020-04-17 | 2020-07-28 | 三一汽车起重机械有限公司 | Steering control system and crane |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1465422A (en) * | 1965-08-06 | 1967-01-13 | Hydraulic steering system including assisted | |
| NL6807776A (en) * | 1968-05-31 | 1969-12-02 |
-
1979
- 1979-11-16 DE DE2946274A patent/DE2946274C2/en not_active Expired
-
1980
- 1980-11-12 DK DK480980A patent/DK149990C/en active
- 1980-11-14 FR FR8024292A patent/FR2470883A1/en active Granted
- 1980-11-14 IT IT68751/80A patent/IT1129859B/en active
- 1980-11-14 GB GB8036591A patent/GB2063192B/en not_active Expired
- 1980-11-14 DD DD80225214A patent/DD154385A5/en unknown
- 1980-11-17 JP JP16092180A patent/JPS5686206A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5686206A (en) | 1981-07-13 |
| DE2946274B1 (en) | 1981-03-26 |
| GB2063192A (en) | 1981-06-03 |
| DD154385A5 (en) | 1982-03-17 |
| GB2063192B (en) | 1983-08-10 |
| DK149990C (en) | 1987-10-12 |
| DK480980A (en) | 1981-05-17 |
| DE2946274C2 (en) | 1981-11-12 |
| FR2470883A1 (en) | 1981-06-12 |
| IT1129859B (en) | 1986-06-11 |
| IT8068751A0 (en) | 1980-11-14 |
| FR2470883B1 (en) | 1984-08-24 |
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