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WO1996001759A1 - Dispositif hydraulique de direction - Google Patents

Dispositif hydraulique de direction Download PDF

Info

Publication number
WO1996001759A1
WO1996001759A1 PCT/DE1995/000925 DE9500925W WO9601759A1 WO 1996001759 A1 WO1996001759 A1 WO 1996001759A1 DE 9500925 W DE9500925 W DE 9500925W WO 9601759 A1 WO9601759 A1 WO 9601759A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
working
steering device
hydraulic steering
steering
Prior art date
Application number
PCT/DE1995/000925
Other languages
German (de)
English (en)
Inventor
Wolfgang Gabriel
Original Assignee
Wolfgang Gabriel
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19944424330 external-priority patent/DE4424330C1/de
Application filed by Wolfgang Gabriel filed Critical Wolfgang Gabriel
Publication of WO1996001759A1 publication Critical patent/WO1996001759A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D3/00—Steering gears
    • B62D3/14—Steering gears hydraulic

Definitions

  • the invention relates to a hydraulic steering device for motor vehicles, in particular for passenger cars, with a steering drive with a working cylinder with a working chamber and a working piston with a piston rod, as well as cylinder bottoms closing the working chamber, in which the piston rod is guided centrally and a cylinder bottom with a cap has a hub with a spindle nut, which is connected to a steering handwheel and in which a threaded spindle is rotatably mounted, which is connected in its axial extension to the piston rod and an anti-rotation device, and finally the other cylinder base has pressure connections which pass through channels are connected to the working chamber and via lines to a steering cylinder.
  • a generic steering device is known from GB-PS 451,224.
  • This steering device known according to the state of the art has the advantage that when the steering handwheel is actuated with rotation of the spindle nut connected to the steering spindle, it moves the piston rod with the working piston attached to it, which means that hydraulically supported steering without pressure support by corresponding pumps pen is possible.
  • the invention proposes, starting from the steering device of the type mentioned, the characterizing features of the main claim.
  • Advantageous embodiments of the invention are described in subclaims 2 to 15.
  • the solution according to the invention creates an overall compact and safe steering drive which is particularly suitable for smaller and light motor vehicles such as for example, cars.
  • this steering drive is characterized by its maintenance-free nature and it can be flexibly coupled to the steering handwheel, which prevents injuries in this area.
  • the piston arrangement which is directly connected to the steering spindle causes the working medium to be pressed through the special upstream channels and the respective tie rod bore into the working chambers in the steering cylinder.
  • no auxiliary worker via pumps is required for this.
  • there is the advantage that all the sensitive parts that belong directly to the working cylinder and that allow the movement and power transmission are arranged within the working cylinder.
  • no supply devices for the production of auxiliary workers, such as pumps or similar devices, or assemblies for the control of valve arrangements that are usually required, are available.
  • a prerequisite for the function of such a steering device is that the working medium is under pressure, so to speak that it is “preloaded”.
  • the rooms, hose and pipelines carrying the working medium must also be completely free of air.
  • the working medium in the working chambers of the working and steering cylinders can be moved into any of the two degrees of freedom of the pistons when the ball screw is rotated and the barrel cylinder is thus displaced.
  • the liquid column is displaced via the pressure connections and corresponding pressure lines into the steering cylinder, as a result of which the pistons are also moved.
  • the steerable wheels connected to the pistons or their piston rods can thus be turned in any desired angle depending on the direction of rotation of the steering handwheel.
  • the steering deflection of the wheels can be varied by means of ball screws of different lengths or stroke lengths of the pistons.
  • the steering device according to the invention can also be reinforced with hydraulic or pneumatic auxiliary forces or with a vacuum, thereby expanding the field of application.
  • the measures provided for in subclaim 2 are suitable for prestressing the working medium in any position of the working piston with a defined pressure.
  • the air cushion present in the auxiliary piston bores in the area of the spring can be used as an auxiliary force, which thus serves to support the spring force.
  • cup springs or other suitable spring elements can also be used.
  • the auxiliary pistons for the pretensioning of the working medium can advantageously be used as signal generators, for example when the working pressure of the working medium drops.
  • the feature in the lower saying 3 suitable.
  • the measures according to subclaim 4 serve to ensure the air exchange of the spaces of the steering drive which are not filled with working medium.
  • the air in these rooms can thus be displaced without counter pressure building up to the working pressure of the working medium.
  • Vents in the cylinder walls outside the working chambers.
  • subclaim 5 The feature of subclaim 5 is provided so that the steering drive can be used at temperatures below the freezing point, for example.
  • the measure of subclaim 6 is suitable for maintaining the auxiliary pistons smoothly and at the same time providing a sealing surface with respect to the bore wall and the tie rod.
  • Appropriate sealing and sliding rings on the contact surfaces between the piston and bore walls increase the effectiveness.
  • the measures according to subclaim 7 are intended to prevent the working pistons from rotating in the respective working chambers when the ball screw drive is actuated to initiate a steering movement.
  • subclaims 8 to 12 are particularly suitable for using the cylinder chambers still present as working chambers for driving additional secondary working or steering cylinders.
  • subclaim 13 In order to avoid sluggishness or to prevent failures of the spindle drive by clamping or pressing the sliding and rotating parts within the working cylinder, the measures of subclaim 13 are particularly suitable.
  • subclaims 14 and 15 contribute to avoiding air pockets in the area of guiding and securing the rotating cylinder in the assembly and jam of the working medium when operating the steering device. Malfunctions are possible without these measures.
  • FIG. 1 shows an axial section through the steering drive according to the invention according to section AA in FIG. 2;
  • FIG. 2 shows a view in the direction H according to FIG. 1; 3 shows a radial section through the steering drive along the section course BB according to FIG. 1;
  • FIG. 5 shows an axial partial section along the section course D - D according to FIG. 2;
  • Figure 6 is a schematic representation of a steering drive with a double-acting steering cylinder, lying transversely to the direction of travel.
  • FIG. 7 shows a schematic illustration of a steering drive with a steering cylinder articulated on one side
  • a working cylinder of a steering device is designated by position 1.
  • the working cylinder 1 has two cylinder chambers 2 and 3, which are separated from one another by an intermediate ring 4.
  • the working cylinder 1 On its left side in the drawing, the working cylinder 1 is closed off with an intermediate ring 5, which is covered with an outer cylinder cover 6. On the axially opposite side of the working cylinder 1, the cylinder chamber 3 is sealed with a cylinder bottom 7.
  • the cross-sectional areas of all the individual elements of the working cylinder 1 are essentially quadratic, the cylinder bore with the cylinder walls 2.1 and 3.1 is usually circular.
  • the outer cross-sectional area makes it possible to arrange tie rod holes 8 to 8.3 over the entire length of the working cylinder 1 in the corner regions, in which tie rods 9 are provided.
  • the tie rods 9 clamp the cylinder chambers 2 and 3 as well as the intermediate rings 4 and 5, the cylinder cover 6 and the cylinder base 7 against each other, whereby a stable unit is formed.
  • cylinder 10 In the interior of the cylinder chambers 2 and 3 there is an axially displaceable cylinder 10, on the axial end of which working pistons 11 and 12 are fastened, for example shrunk on.
  • the cylinder surfaces of the working pistons 11 and 12 are arranged in a known manner in a liquid-tight but displaceable manner with respect to the walls 2.1 and 3.1 of the cylinder chambers 2 and 3.
  • Working chambers I and II are thus formed between the pistons 11 and 12 and the intermediate ring 4.
  • the cylinder 10 is also sealingly guided on its outer surface with respect to a guide 4.1 provided in the intermediate ring 4.
  • the cylinder 10 is also axially partially guided on a guide 13 designed as an anti-rotation device, which is fastened in the cylinder base 7.
  • the guide 13 On its outer surface, the guide 13 has a geometry that deviates from the cylinder shape and is, for example, hexagonal (FIG. 4).
  • the individual surfaces of the guide 13 preferably run axially parallel.
  • the cylinder 10 is substantially tubular with an inner surface adapted to the guide 13. This makes it possible to move the cylinder 10 with the pistons 11 and 12 in the working chambers I and II in a rotationally secure manner.
  • a ball screw nut 15 is inserted axially in the cylinder 10, whose balls 16 in conjunction with a corresponding ball screw spindle 17 allow the cylinder 10 with its working pistons 11 and 12 to move when the ball threaded spindle 17 is rotated.
  • the ball screw 17 is rotatable in a bearing 18 between the hissing ring 5 and the cylinder base 6 and is mounted so as to be non-displaceable in the axial direction and sealed against loss of liquid, for example with sealing rings 19, and connected in the further course to a conventional, but not shown, steering handwheel.
  • Auxiliary piston bores 20.1 and 20.2 are arranged in the tie rod bores 8.1 and 8.2 in the area of the cylinder chamber, in which auxiliary pistons 21.1 and 21.2 are each displaceably arranged against a spring 22.1 and 22.2 resting on the intermediate ring 5.
  • the auxiliary pistons 21.1 and 21.2 are sealed with mechanical seals against the wall of the auxiliary piston bore 20.1 and 20.2 and against the tie rod 9, for which purpose the corresponding surfaces are ground.
  • the auxiliary piston bore 20.1 is connected to a pressure connection 23 via the tie rod bore 8.1 and via an overflow channel 24 introduced into the cylinder base 7.
  • the pressure connection 23 is not described in more detail connected to the cylinder base 7.
  • the tie rod bore 8.1 is connected to the working chamber II of the working cylinder 1 via an overflow channel 28.1 in the intermediate ring 4.
  • the auxiliary piston bore 20.2 is in accordance with the lower sectional view of FIG. 1 via the tie rod bore 8.2 with a pressure connection 25, not described in detail, via a further overflow channel 26.
  • a connection from the pressure connection 25 to the working chamber I there is a connection from the pressure connection 25 to the working chamber I.
  • an overflow channel 28.2 is provided in the intermediate ring 4 within a bore 27 receiving the tie rod 9, which opens into the tie rod bore 8.2.
  • sealing rings 29 to 31 are provided between all the individual components, which prevent the working medium from leaking out of the working chambers I and II and that, in addition, the working cylinder 1 is sealed as a whole.
  • FIG. 5 shows the connection between the spaces of the cylinder chambers 2 and 3 lying on the outside according to the drawing, which serves to exchange air when the working pistons 11 and 12 move.
  • overflow channels 33 and 34 are introduced in the intermediate ring 5 and in the cylinder bottom 7 such that they have an opening in the respective interior of the cylinder chambers 2 and 3 and the other opening in the passage for the tie rod 9 in the tie rod bore 8.3.
  • FIGS. 6 and 7 show steering drives which are shown very schematically and show two possible uses in connection with different types of steering cylinders.
  • the pressure connections 23 and 25 on the working cylinder 1 are arranged radially on the respective working chambers I and II for simpler illustration.
  • the pressure connections 23 and 25 are connected via partly rigid and partly flexible line connections to a steering cylinder 40 arranged transversely to an assumed direction of travel and its working piston 41.
  • the steering cylinder 40 is connected in a conditionally movable manner at a bearing point 42 to a rigid front axle 43, shown here, of a vehicle (not designated in any more detail).
  • a double-acting piston rod 44 is articulated at its distal end, which is located outside the steering cylinder 40, to a steering lever 45, which is connected to a steering knuckle 46 each of the steerable wheels 47.
  • a steering cylinder 50 is arranged, for example, on a side of the vehicle in the direction of action of its working piston 51, which is longitudinal to the direction of travel, with a piston rod 52.
  • the piston rod 52 is connected to a steering lever 53 which is connected to a track lever 54.
  • the track lever 54 is in turn connected via a tie rod 55 to a steering lever 56, which in turn is connected to a steering knuckle 57 of wheels 59 which are also articulated on a rigid axle 58.
  • the steering knuckle 57 of the left-hand wheel 59 in the drawing is connected to the track lever 54.
  • Example 2 According to FIGS. 8 and 9, in addition to the means described according to embodiment 1, a sealing washer 60 is arranged within the guide bore of the barrel 10 between the axially opposite ends of the guide 13 and the ball screw 17.
  • the sealing disk 60 thus forms a media-tight closure of the guide bore, as a result of which an additional working chamber III between the intermediate ring 5 and the piston 11 on one side and an additional working chamber IV between the cylinder base 7 and the piston 12 the other side of the working cylinder 1 are formed.
  • the sealing disk 60 can advantageously be designed like a conventional hydraulic piston. It is used essentially free-standing, but must be designed to be sealed and at the same time sliding on the wall of the barrel 10 so that the barrel 10 is sufficiently movable and the function is guaranteed.
  • a radial bore 61 is arranged in the wall of the working chamber III near the intermediate ring 5, which is connected in a conventional manner to a further secondary working cylinder (not shown) via a pressure connection 62.
  • the bore 61 and the pressure connection 62 can also alternatively be connected in a correspondingly sealed manner to the working chamber III, for example in the intermediate ring 5 and through the cylinder base 6 (not shown).
  • the working chamber IV has a bore 63 and a pressure connection 64, which are advantageously arranged on the cylinder base 7 and a di enable correct media supply and discharge in and out of the Work Chamber IV.
  • the two tie rod bores 8 and 8.3 are respectively provided with auxiliary piston bores 20.3 and 20.4 and with auxiliary pistons 21.3 and 21.4 with spring elements 22.3 and 22.4.
  • the auxiliary piston bore 20.3 assigned to the working chamber III is rotated by 180 ° with respect to the other bores.
  • bores 65 and 66 are provided, which produce a connection for the pressure medium between the auxiliary piston bores 20.3 and 20.4 via the tie rod bores 8 and 8.3 with the respective working chambers III or IV.
  • These bores 65 and 66 are preferably made outside the stroke of the pistons 11 and 12 in the area of the intermediate ring 5 or the cylinder base 7 and in a bore axis inclined to the cylinder axis or radially in the respective cylinder wall.
  • an axial bore 67 can be provided, which begins on the end face of the guide 13 in the area of the sealing disk 60 and ends in a radial bore, which opens into the work chamber IV in the area of the cylinder base 7 and prevents the occurrence of congestion Moving the barrel 10 is useful.
  • the guide 13 is radially movable to a limited extent in order to avoid jamming during the movement of the barrel cylinder 10.
  • an elastic connection 68 between the guide 13 and The cylinder base 7 is provided, which allows the guide 13 to move radially with a high degree of rotation.
  • the spindle 17 or the ball screw nut 15 can be flexibly mounted.
  • the measures for air balance between the working chambers III and IV are omitted.
  • the respective bore 33 in the intermediate ring 5 and the bore 34 in the cylinder base 7 are not introduced.
  • the area of application of the steering device can thus be expanded.
  • a four-acting working cylinder can also advantageously be used for multiple steering systems.
  • other applications in the field of hydraulics or pneumatics are possible.
  • the cylinder 10 is moved in the left-hand direction according to the drawing (see FIG. 1).
  • a pre-stressed working medium located in the working chamber II can be displaced and can pass through the overflow channel 28.1 and through the tie rod bore 8.1 through the overflow channel 24 into the pressure connection 23.
  • the liquid column is fed, for example, to the steering cylinder 40 through appropriate pressure pipes and partially flexible pressure hoses.
  • the working piston 41 is acted upon and initiates a corresponding steering movement of the wheels 47 via the piston rod 42, the steering lever 45 and the steering knuckle 46.
  • the liquid column located in the other working chamber of the steering cylinder 40 is shifted in the opposite direction via the other lines and the pressure connection 25, using the tensile forces generated.
  • the working medium is constantly biased in the respective auxiliary piston bores 20.1 and 20.2 by the auxiliary pistons 21.1 and 21.2 and the springs 22.1 and 22.2, whereby an immediate transmission of movement from the respective working piston 11 or 12 to the steerable wheels is possible.
  • Steering ratios that differ from one another can be achieved by different pitches of the ball screw drive in the working cylinder 1 or differently effective piston surfaces of the working cylinders communicating with one another.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Power Steering Mechanism (AREA)

Abstract

Un dispositif hydraulique de direction pour véhicules à moteur, notamment des voitures particulières, comprend une direction assistée ayant un cylindre de travail avec une chambre de travail et un piston de travail avec une tige, ainsi que des fonds de cylindre qui délimitent la chambre de travail et dans lesquels la tige de piston est centralement guidée. Un fond du cylindre comprend une calotte avec un moyeu et un écrou d'arbre relié à un volant et dans lequel un arbre fileté est monté rotatif. Dans son prolongement axial, l'arbre fileté est relié à la tige de piston et à un dispositif anti-torsion. L'autre fond du cylindre est pourvu de raccords de pression en communication par des conduits avec la chambre de travail et par des lignes de pression avec un vérin de braquage. L'objet de l'invention est de développer un dispositif de direction du type décrit, de façon à élargir son champ d'application, augmenter sa fiabilité et sa sécurité et minimiser les frais d'entretien. A cet effet, un cylindre de travail (1) comprend plusieurs chambres de travail (I - IV) mutuellement séparées dans lesquelles des pistons de travail mobiles (11, 12) sont assujettis de façon à ne pas tourner et coopèrent de manière connue en soi à travers un système de canaux et sans pression auxiliaire avec des roues susceptibles d'être dirigées par des vérins de braquage.
PCT/DE1995/000925 1994-07-11 1995-07-10 Dispositif hydraulique de direction WO1996001759A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DEP4424330.8 1994-07-11
DE19944424330 DE4424330C1 (de) 1994-07-11 1994-07-11 Hydraulische Lenkeinrichtung
DE19522057.9 1995-06-17
DE1995122057 DE19522057C1 (de) 1994-07-11 1995-06-17 Hydraulische Lenkeinrichtung

Publications (1)

Publication Number Publication Date
WO1996001759A1 true WO1996001759A1 (fr) 1996-01-25

Family

ID=25938223

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1995/000925 WO1996001759A1 (fr) 1994-07-11 1995-07-10 Dispositif hydraulique de direction

Country Status (2)

Country Link
DE (1) DE19522057C1 (fr)
WO (1) WO1996001759A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1911659A3 (fr) * 2006-10-13 2010-01-20 Hitachi, Ltd. Système de direction

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB451224A (en) * 1935-01-31 1936-07-31 Ronald Scaife Hydraulic steering control for vehicles
GB997804A (en) * 1964-04-29 1965-07-07 Ford Motor Co Motor vehicle steering system

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4424330C1 (de) * 1994-07-11 1995-12-21 Wolfgang Gabriel Hydraulische Lenkeinrichtung

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB451224A (en) * 1935-01-31 1936-07-31 Ronald Scaife Hydraulic steering control for vehicles
GB997804A (en) * 1964-04-29 1965-07-07 Ford Motor Co Motor vehicle steering system

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1911659A3 (fr) * 2006-10-13 2010-01-20 Hitachi, Ltd. Système de direction
US8066091B2 (en) 2006-10-13 2011-11-29 Hitachi, Ltd. Steering system

Also Published As

Publication number Publication date
DE19522057C1 (de) 1996-09-19

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