WO2014115483A1 - インテグラル型パワーステアリング装置 - Google Patents
インテグラル型パワーステアリング装置 Download PDFInfo
- Publication number
- WO2014115483A1 WO2014115483A1 PCT/JP2013/085060 JP2013085060W WO2014115483A1 WO 2014115483 A1 WO2014115483 A1 WO 2014115483A1 JP 2013085060 W JP2013085060 W JP 2013085060W WO 2014115483 A1 WO2014115483 A1 WO 2014115483A1
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- WO
- WIPO (PCT)
- Prior art keywords
- valve
- type power
- power steering
- integral type
- pressure chamber
- Prior art date
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Classifications
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- 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
- B62D5/20—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle specially adapted for particular type of steering gear or particular application
- B62D5/22—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle specially adapted for particular type of steering gear or particular application for rack-and-pinion type
-
- 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
- B62D5/061—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle provided with effort, steering lock, or end-of-stroke limiters
-
- 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
- B62D5/07—Supply of pressurised fluid for steering also supplying other consumers ; control thereof
-
- 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
- B62D5/08—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 type of steering valve used
- B62D5/083—Rotary valves
-
- 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
- B62D5/08—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 type of steering valve used
- B62D5/087—Sliding spool valves
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- 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
- B62D5/10—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 type of power unit
- B62D5/12—Piston and cylinder
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- 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
- B62D5/20—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle specially adapted for particular type of steering gear or particular application
- B62D5/24—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle specially adapted for particular type of steering gear or particular application for worm type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/44—Mechanical actuating means
- F16K31/48—Mechanical actuating means actuated by mechanical timing-device, e.g. with dash-pot
Definitions
- the present invention relates to an integral type power steering apparatus applied to, for example, a relatively large vehicle, which includes a stroke limiter for limiting the stroke of a piston.
- the gear is formed by a housing body composed of a substantially bottomed cylindrical gear housing, a valve housing that closes the opening of the gear housing, and a piston linked to a steering shaft.
- the housing is divided into two pressure chambers and generates a steering assist torque.
- the power cylinder is provided in the valve housing, and is steered to each pressure chamber of the power cylinder according to the steering direction and torque.
- a rotary valve that selectively supplies an appropriate hydraulic pressure for generating assist torque, and a pair of first and second valves that are stroke limiters that regulate the stroke position of the piston are the first and second valves, respectively. It is provided to face the second pressure chamber.
- Each of the first and second valves is configured such that a valve body is accommodated in a valve accommodating hole provided in each housing, and a valve body is slidably disposed on the inner peripheral side of the valve body.
- the piston presses against the pin member linked to each valve body to open the valve, thereby communicating the pressure chambers with each other. Excessive rises are suppressed.
- valve body and the like are accommodated in the respective housings via the valve body, and the valve body and the valve body and the like are arranged in the radial direction. Since it is provided to be polymerized, the diameter of the valve housing hole is inevitably increased for each of the above valves.
- the rotary valve is provided in the central portion on the inner peripheral side of the valve housing, making it difficult to place the first valve sufficiently close to the inner peripheral side.
- the valve housing has been increased in size, and consequently the housing body has been increased in size.
- valve housing hole is provided obliquely with respect to the axis of the steering shaft, the range occupied by the valve housing hole in the radial direction of the valve housing becomes large.
- the valve housing has been increased in size.
- the present invention has been devised in view of such problems, and provides an integral type power steering device capable of reducing the size of a housing body.
- the first aspect of the present invention is the first valve housing hole formed by machining the valve housing itself, and the first valve disposed at least on the valve housing side, and the first valve housing hole.
- a first valve seat portion provided on the first pressure chamber side and having a first pin insertion hole penetratingly formed along an axial direction on an inner peripheral side thereof; and the first valve seat portion in the first valve housing hole
- a first valve body which is provided so as to be movable in an axial direction so as to face the first valve body and blocks movement of hydraulic oil from the second pressure chamber side to the first pressure chamber side by being seated on the first valve seat portion;
- the first valve body is configured integrally with the first valve body, faces the first pressure chamber through the first pin insertion hole, and is pressed by the piston when the piston reaches the first predetermined position.
- a first pin portion for applying a moving force to The serial first valve body is characterized by being configured by a first biasing member for biasing the said first valve seat portion.
- the invention according to claim 11 is, in particular, a first valve housing hole provided at least on the valve housing side, provided in the valve housing and configured to substantially coincide with the moving direction of the piston;
- a first valve seat provided on the first pressure chamber side in the first valve housing hole and having a first pin insertion hole penetratingly formed along the axial direction on the inner circumferential side thereof; and in the first valve housing hole And is provided so as to be movable in the axial direction so as to face the first valve seat portion, and the movement of hydraulic oil from the second pressure chamber side to the first pressure chamber side is blocked by being seated on the first valve seat portion.
- the first valve body is configured integrally with the first valve body, faces the first pressure chamber through the first pin insertion hole, and is pressed by the piston when the piston reaches the first predetermined position.
- a first pin portion which imparts motive power, and the first valve body is characterized in that it is constituted by a first urging member for urging the first valve seat portion.
- the valve body and the valve body are radially arranged in the valve housing.
- the radial dimension of the first valve housing hole can be set smaller than in the conventional case where the polymerization is related.
- the first valve housing hole can be disposed closer to the rotary valve side, and as a result, the valve housing (housing body) can be reduced in size.
- the range occupied by the first valve housing hole in the radial direction of the valve housing can be reduced. it can.
- the first valve housing hole can be disposed closer to the rotary valve side, and as a result, the valve housing (housing body) can be reduced in size.
- FIG. 1 is a longitudinal sectional view showing a first embodiment of an integral power steering apparatus according to the present invention. It is an enlarged view of the 1st valve
- the integral type power steering device 1 includes a substantially bottomed cylindrical gear housing 2 in which a cylinder portion 2a is formed, and one end portion of the cylinder portion 2a.
- a valve housing 4 that closes the opening and forms the housing body 3 (housing) together with the gear housing 2, one end is pivotally supported in the valve housing 4, and the other end is inserted and disposed in the cylinder portion 2 a.
- a steering shaft 5 and an outer periphery of the other end of the steering shaft 5 are provided so as to be axially movable via a ball screw mechanism 6 as a first conversion mechanism, and are slidably accommodated in the cylinder portion 2a.
- the piston 7 that divides the inside of the gear housing 2 into the first pressure chamber P1 and the second pressure chamber P2 and one end side thereof are linked to the piston 7 via the second conversion mechanism, It has a sector shaft 8 for steering via the unillustrated pitman arm by rotating along with the axial movement of the piston 7, the.
- One end of the steering shaft 5 is linked to a steering wheel (not shown), and the other end is provided on an axis of the input shaft 9 that is pivotally supported by the valve housing 4.
- One end of the steering shaft 5 is connected to the input shaft 9.
- An output shaft 10 that is superposed on the outer periphery and is linked to the piston 7 on the other end side is connected to the output shaft 10 via a torsion bar 11 so as to be relatively rotatable.
- the piston 7 moves in the axial direction as the output shaft 10 rotates by being linked to the output shaft 10 via the ball screw mechanism 6.
- a rack gear 7a (tooth portion) is formed on the side of the piston 7, and the rack gear 7a meshes with a sector gear 8a on one end of the sector shaft 8. That is, the gears 7a and 8a constitute a second conversion mechanism, and the axial movement of the piston 7 is converted into rotation of the sector shaft 8 by the second conversion mechanism.
- the gear housing 2 is formed of a metal material, and is provided with a sector gear housing portion that is provided in a form orthogonal to the cylinder portion 2a and communicates with the cylinder portion 2a and houses the sector gear 8a. 2b.
- the valve housing 4 is made of a metal material, and a rotary valve accommodating portion 4a (shaft insertion hole) is formed through the inner axial direction.
- the rotary valve accommodating portion 4a accommodates the other end portion of the input shaft 9 and one end portion of the output shaft 10 in the form of overlapping in the radial direction, and the rotary valve 17 is accommodated by the overlapping portion of the shafts 9 and 10. It is configured.
- valve housing 4 is configured as a fitting convex portion 4b in which the inner end side accommodated in the cylinder portion 2a is formed in a stepped diameter reducing shape, while a step is formed at the opening end portion of the cylinder portion 2a.
- a fitting recess 2d formed in an enlarged shape is provided.
- the fitting projection 4b and the fitting recess 2d are concavo-convexly fitted, whereby the opening of the cylinder portion 2a is closed by the valve housing 4.
- An annular holding groove 12 is formed on the outer peripheral surface of the fitting convex portion 4b, and a seal ring 13 is fitted and held in the holding groove 12.
- an IN port 14 that communicates with an oil pump (hydraulic power source) (not shown), and a hydraulic pressure introduced from the IN port 14 is supplied and discharged to the pressure chambers P 1 and P 2.
- a port 15 and an OUT port 16 for discharging hydraulic oil discharged from the pressure chambers P1 and P2 through the supply / discharge port 15 to a reservoir tank (not shown) are provided.
- the supply / discharge port 15 communicates with the first pressure chamber P1 via the first oil passage L1 provided in the output shaft 10 and also passes through the second oil passage L2 provided in the gear housing 2 and the like. And communicates with the second pressure chamber P2.
- the rotary valve 17 is switched according to the rotation direction of the steering wheel, and the hydraulic pressure discharged from the oil pump is changed to the first pressure chamber P1 and the second pressure chamber P2. Is selectively supplied to either one of the two pressure chambers P1 and P2, and the other one of the pressure chambers P1 and P2 is connected to the reservoir tank, and the piston 7 is moved by the differential pressure between the pressure chambers P1 and P2. Is to be added.
- valve housing 4 is disposed on the outer peripheral side of the rotary valve housing portion 4 a on the one end side of the piston 7 at a position facing the piston head on one end side of the piston 7.
- a first valve 18 is provided as a stroke limiter for limiting the stroke amount.
- the bottom valve 2c of the gear housing 2 is also provided with a second valve 19 as a stroke limiter for limiting the stroke amount on the other end side of the piston 7 at a position facing the piston head on the other end side of the piston 7. ing.
- the first and second valves 18 and 19 are connected to each other by a communication passage 20 formed so as to straddle the gear housing 2 and the valve housing 4.
- the first valve 18 is formed in the valve housing 4 and has a first valve housing hole 21 whose one end side (the lower side in FIGS. 1 and 2) communicates with the first pressure chamber P1. And a sealing plug 22 that closes the other end of the first valve housing hole 21, and the first valve housing hole 21 is slidably disposed on the inner peripheral surface of the first valve housing hole 21.
- a first coil spring 25 as a first urging member disposed on the other end side of the first valve housing hole 21 and urging the first valve body 23 toward the first valve seat member 24 side, and one end side thereof
- a first pin 26 (first pin portion) is fixed to the first valve body 23 and the other end faces the first pressure chamber P1.
- the first valve housing hole 21 includes a first large diameter portion 27 (large diameter portion) in which the first valve body 23 and the first valve seat member 24 are accommodated, and a first large diameter portion 27 to a first portion.
- the first small-diameter portion 28 (small-diameter portion) that is formed with a reduced diameter toward the pressure chamber P1 and through which the first pin 26 is inserted, is interposed between the first large-diameter portion 27 and the first small-diameter portion 28.
- the first valve seat member 24 is arranged so as to abut against the formed stepped portion 21a.
- the axis of the first valve housing hole 21 is set substantially parallel to the axis of the steering shaft 5.
- the said step part 21a can be easily formed by forming the said 1st valve
- the first valve body 23 is provided on one end side which is the first valve seat member 24 side, and has a small diameter cylindrical portion 23a which is set slightly smaller than the inner diameter of the first large diameter portion 27, and the other end side.
- the outer peripheral surface of the first large-diameter portion 27 is composed of a large-diameter cylindrical portion 23b that is in sliding contact with the inner peripheral surface of the first large-diameter portion 27. 29 is formed.
- the through hole 29 is configured as a small diameter hole 29a in which the inner peripheral side of the small diameter cylindrical portion 23a is set to an inner diameter smaller than the outer diameter of the first pin 26, and one end side of the first pin 26 is press-fitted and fixed. It has a structure.
- the inner peripheral side of the large diameter cylindrical portion 23b is configured as a large diameter hole 29b having an inner diameter larger than that of the small diameter hole 29a.
- a spring seat 29c on which the first coil spring 25 is seated is formed at the inner end of the large diameter hole 29b.
- the first coil spring 25 is configured such that one end portion on the first pressure chamber P1 side is seated on the spring seat portion 29c and the other end portion is seated on the inner end surface of the sealing plug 22. It is accommodated and held in one valve accommodating hole 21.
- the sealing plug 22 has a large-diameter portion 22a facing the outside of the housing and a small-diameter portion 22b having an outer diameter smaller than the large-diameter portion 22a, and a male screw portion formed on the outer periphery of the small-diameter portion 22b.
- the first large diameter portion 27 is screwed into a female screw portion formed on the inner periphery.
- an engaging portion 22c to which a tool (specifically, a hexagon wrench) for attaching and detaching the sealing plug 22 is engaged is recessed at a substantially central position of the outer end surface of the large diameter portion 22a.
- a seal ring 30 is fitted on the outer periphery of the base end portion of the small diameter portion 22b, and the inside and outside of the first valve housing hole 21 are liquid-tightly sealed by the seal ring 30.
- the first valve seat member 24 is mounted on a cylindrical first seat member 31 on which the first valve body 23 is seated, and an inner peripheral surface of the first seat member 31.
- a cylindrical first guide member 33 having a guide hole 32 (first pin insertion hole) penetratingly formed in the axial direction.
- the first sheet member 31 has an outer diameter larger than that of the small diameter cylindrical portion 23a and an inner diameter slightly smaller than that of the large diameter cylindrical portion 23b, and is press-fitted into the inner end portion of the first large diameter portion 27. ing. Further, the first sheet member 31 is formed with an inner peripheral taper portion 31a and an outer peripheral taper portion 31b on the outer inner peripheral portion so that the substantially central portions in the radial direction at both ends thereof are convex, and both the tapered portions 31a. 31b, the inner peripheral tapered portion 31a facing the first valve body 23 functions as a seat surface against which the tip of the small diameter cylindrical portion 23a comes into contact. On the other hand, the first pressure chamber P1 side of the first seat member 31 abuts on the stepped portion 21a, and the outer peripheral tapered portion 31b inserts the first valve seat member 24 into the first valve accommodating hole 21. Contributes to improved insertability.
- the first guide member 33 is formed to be shorter in the axial direction than the first sheet member 31, and has a plurality of introduction holes on the outer peripheral side of the guide hole 32 along with the guide hole 32 along the internal axial direction. 34 are provided substantially evenly in the circumferential direction. As a result, when the first valve 18 is opened, hydraulic oil flows through the introduction holes 34.
- the first pin 26 is formed in a rod shape as shown in FIG. 2 and is slidably supported by the first guide member 33.
- the front end surface 26a of the first pin 26 is in contact with the piston head at one end of the piston 7 shown in FIG. 1 at the stroke allowable limit (first predetermined position) of the piston 7. Is set to a proper protruding amount.
- the first pin 26 has a hemispherical shape as shown in FIG. 4A, in which the front end surface 26a employed in the present embodiment is formed in a flat shape, and the entire front end portion shown in FIG. 4B is formed in a hemispherical shape.
- the thing which comprised only the front end surface 26a shown to (B) in spherical shape, etc. can be considered.
- the second valve 19 includes a second valve housing portion 2e formed in the bottom portion 2c, and a cylindrical valve case 35 screwed into the second valve housing portion 2e.
- a second valve accommodating hole 36 formed in the inner periphery of the bottom side of the valve case 35, a second valve element 37 slidably accommodated in the second valve accommodating hole 36, and the second valve element
- the second valve seat member 38 is press-fitted and fixed to the opening end side of the second valve housing hole 36 across the 37, and is disposed on the bottom side of the second valve housing hole 36 across the second valve body 37.
- a second coil spring 39 as a second urging member for urging the two-valve body 37 to the second valve seat member side 38, one end side is fixed to the second valve body 37, and the tip on the other end side is the above-mentioned And a second pin 40 facing the second pressure chamber P2.
- the valve case 35 includes a hollow small-diameter shaft portion 35a in which the second valve housing hole 36 is formed, and a solid large-diameter portion 35b having a diameter larger than that of the small-diameter shaft portion 35a.
- the male screw portion formed on the outer periphery of the base end portion of the small-diameter shaft portion 35a is fixedly attached to the gear housing 2 by screwing with the female screw portion formed on the inner periphery of the outer end side of the second valve housing portion 2e. ing.
- a through-hole 41 communicating with the inner and outer circumferences is formed in the axially intermediate position of the small-diameter shaft portion 35a along the radial direction.
- the hydraulic oil passes through the through-hole 41. Will flow.
- seal rings 42 and 43 are fitted on the outer periphery of the base end portion and the substantially central periphery of the small-diameter shaft portion 35a, and the inside and outside of the second valve housing portion 2e are liquid-tight by the seal rings 42 and 43, respectively. Is sealed.
- a valve seat accommodating portion 36a having a larger diameter than the side accommodating the second valve element 37 is formed on the inner periphery of the opening end side of the second valve accommodating hole 36, and the valve seat accommodating portion 36a
- the valve chamber 2e communicates with the second pressure chamber P2 through a small-diameter hole 44 formed through the inner end wall.
- the second valve body 37 is provided on one end side that is the second valve seat member 38 side, and has a small diameter cylindrical portion 37a that is set slightly smaller than the inner diameter of the second valve housing hole 36, and the other end side.
- a large-diameter cylindrical portion 37b whose outer peripheral surface is in sliding contact with the inner peripheral surface of the second valve housing hole 36, and a series of through-holes along the axial direction is formed on the inner peripheral side. 45 is formed. Accordingly, the second valve body 37 is stabilized in posture within the second valve accommodating hole 36 by the large diameter cylindrical portion 37b, and the small diameter cylindrical portion 37a and the second valve accommodating hole are stabilized.
- a passage C ⁇ b> 2 through which hydraulic oil passes is formed between the inner peripheral surface of 36.
- the through hole 45 is configured as a small diameter hole 45a in which the inner peripheral side of the small diameter cylindrical portion 37a is set to an inner diameter smaller than the outer diameter of the second pin 40, and one end side of the second pin 40 is press-fitted and fixed. It has a structure.
- the inner peripheral side of the large diameter cylindrical portion 37b is configured as a large diameter hole 45b having an inner diameter larger than that of the small diameter hole 45a.
- a spring seat 45c on which the second coil spring 39 is seated is formed at the inner end of the large diameter hole 45b.
- the second coil spring 39 is configured such that one end portion on the second pressure chamber P2 side is seated on the spring seat portion 45c and the other end portion is seated on the inner peripheral side end wall of the valve case 35. It is accommodated and held in the second valve accommodation hole 36.
- the second valve seat member 38 is mounted on a cylindrical second seat member 46 on which the second valve body 37 is seated, and an inner peripheral surface of the second seat member 46, and is formed to penetrate in the inner axial direction. And a cylindrical second guide member 47 having a guide hole 48.
- the second seat member 46 has an outer diameter larger than the small diameter cylindrical portion 37a and an inner diameter slightly smaller than the large diameter cylindrical portion 37b, and is accommodated in the second valve accommodating hole 36. Further, the second sheet member 46 is formed with an inner peripheral taper portion 46a and an outer peripheral taper portion 46b on the outer inner peripheral portion so that the substantially central portions in the radial direction at both ends thereof are convex, and both the tapered portions 46a. 46b, the inner peripheral tapered portion 46a facing the second valve body 37 functions as a seat surface against which the tip 37c of the small diameter cylindrical portion 37a abuts. The second seat member 46 is caulked and fixed to the end of the valve case 35 on the second pressure chamber P2 side at the end of the second pressure chamber P2.
- the second guide member 47 is formed to have a smaller axial length than the second sheet member 46, and has a plurality of introduction holes on the outer peripheral side of the guide hole 48 along with the guide hole 48 along the inner axial direction. 49 are provided substantially evenly in the circumferential direction. As a result, when the second valve 19 is opened, the hydraulic oil flows through the introduction holes 49.
- the second pin 40 is formed in a rod shape and is slidably supported by the second guide member 47.
- the tip surface 40a of the second pin 40 is in contact with the piston head on the other end side of the piston 7 shown in FIG. 1 at the stroke allowable limit (second predetermined position) of the piston 7.
- the amount of protrusion is set.
- the second pin 40 is similar to the first pin 26 shown in FIG. 4 except that the tip surface 40a employed in the present embodiment shown in FIG. A configuration in which the entire tip is configured in a hemispherical shape, a configuration in which only the tip surface 40a shown in FIG.
- the second valve body 37, the second valve seat member 38, the second coil spring 39, and the second pin 40 are previously accommodated in the valve case 35, and in a so-called unitized state, the second valve accommodating portion 2e. As a result, the assembly workability can be improved.
- the second valve body 37 is By moving to the lower end side against the urging force of the coil spring 39, the tip 37c is separated from the second sheet member 46, and the hydraulic pressure in the second pressure chamber P2 flows into the passage C2 through the introduction hole 49, The fluid flows from the passage C2 to the first valve 18 through the through hole 41 and the communication passage 20.
- the piston 7 is greatly displaced toward the upper end side, and the tip surface 26a of the first pin 26 comes into contact with the piston head on the one end side.
- the first valve body 23 is pushed together with the first pin 26 in the displacement direction of the piston 7, and the tip 23 c is separated from the first sheet member 31.
- the first pressure chamber P1 and the second pressure chamber P2 communicate with each other, and the hydraulic oil in the second pressure chamber P2 is discharged to the first pressure chamber P1.
- the oil pressure decreases, and an excessive increase in the oil pressure in the first pressure chamber P1 is suppressed.
- the first valve body 23 moves to the upper end side against the urging force of the first coil spring 25, so that the tip 23c is moved.
- the hydraulic oil in the first pressure chamber P ⁇ b> 1 flows away from the first seat member 31 to the passage C ⁇ b> 1 through the introduction hole 34, and flows from the passage C ⁇ b> 1 to the second valve 19 side through the communication passage 20. To do.
- the piston 7 is greatly displaced toward the lower end side, and the tip surface 40a of the second pin 40 contacts the piston head on the other end side.
- the second valve body 37 is pushed together with the second pin 40 in the displacement direction of the piston 7, and the tip 37 c is separated from the second sheet member 46.
- the first pressure chamber P1 and the second pressure chamber P2 communicate with each other, and the hydraulic oil in the first pressure chamber P1 is discharged to the second pressure chamber P2.
- the first pressure chamber P1 The oil pressure decreases, and an excessive increase in the oil pressure in the first pressure chamber P1 is suppressed.
- the first valve 18 and the second valve 19 as stroke limiters cause an excessive increase in the hydraulic pressure in the first pressure chamber P1 and the second pressure chamber P2.
- the transmission mechanism and the like are protected.
- the contact position of the first and second pins 26 and 40 with the piston 7 is set as follows. That is, in a state where it is not connected to the pump, the front end surfaces 26a, 40a of the first and second pins 26, 40 are projected in advance to the piston 7 side sufficiently more than the appropriate amount, By operating the steering wheel, the piston 7 is brought into contact with the front end surfaces 26a and 40a, and the first and second pins 26 and 40 are pushed into the through holes 29 and 45, respectively. Thereby, the position adjusting operation of the first pin 26 and the second pin 40 for operating the first and second valves 18 and 19 can be performed easily and accurately.
- the first valve 18 on the valve housing 4 side is connected to the valve housing 4 without using a case member such as the valve case 35.
- the configuration is directly provided.
- the valve body side valve is attached via a valve body corresponding to the valve case 35, that is, the valve body is compared with the conventional valve body and the valve body are superposed in the radial direction.
- the maximum diameter dimension t1 of the first valve housing hole 21 can be set smaller by the radial width thickness of the first valve housing hole 21.
- the first valve housing hole 21 can be arranged closer to the rotary valve 17 side.
- the valve housing 4 can be reduced in size, and the housing can be reduced based on the downsizing of the valve housing 4.
- the main body 3 can be downsized.
- the assembly of the second valve 19 can be made efficient in assembling work.
- the through hole corresponding to the first valve housing hole 21 is oblique to the axis of the steering shaft.
- the range occupied by the first valve accommodating hole 21 in the radial direction of the valve housing 4 can be reduced. Therefore, from this point of view, it is possible to dispose the first valve accommodating hole 21 closer to the rotary valve 17 side, and as a result, the valve housing 4 can be reduced in the radial direction.
- the first valve housing hole 21 is disposed substantially parallel to the axis of the steering shaft 5 so that the moving direction of the first pin 26 substantially matches the moving direction of the piston 7. It has become. Therefore, the load acting on the first pin 26 can be reduced and the durability of the first pin 26 can be improved as compared with the conventional case where the moving direction of the pin is different from the moving direction of the piston.
- first seat member 31 is configured to abut on the stepped portion 21 a provided directly on the valve housing 4.
- the displacement of the first valve seat member 24 such as dropping of the first valve seat member 24 due to the hydraulic pressure of the second pressure chamber is suppressed as compared with the conventional case where the valve seat member is caulked and fixed to the valve body.
- the first pin 26 can be supported in a more stable posture, and the durability of the first pin 26 can be further improved.
- the tip surface 26a of the first pin 26 is set so that the center thereof is in contact with the piston head of the piston 7. As a result, the force acting on the first pin 26 from the piston 7 can be received and dispersed by the entire first pin 26, and the durability can be further improved.
- the sealing plug 22 has a large-diameter portion 22a exposed to the outside of the valve housing 4, and is engaged with a tool for attaching / detaching the sealing plug 22 to the outer end surface of the large-diameter portion 22a.
- the portion 22c is configured to be recessed. Thereby, after suppressing the enlargement of the said 1st large diameter part 27 whole, the engaging part 22c with a tool is securable.
- the engaging portion 22c is formed on the outer end surface of the large diameter portion 22a, the tool and the input shaft 9 and the like are compared with the case where the engaging portion 22c is formed on the outer peripheral surface of the large diameter portion 22a. Interference with can also be avoided.
- the inner end portion of the valve housing 4 is reduced in diameter to form the fitting convex portion 4b, while the opening end portion of the gear housing 2 is enlarged in diameter to receive the fitting convex portion 4b.
- the fitting recess 2d is formed, and the housings 2 and 4 are overlapped in the axial direction by the concave and convex fitting between the fitting convex portion 4b and the fitting concave portion 2d. Therefore, the outer diameter of the open end of the gear housing 2 can be reduced by the amount of polymerization in the axial direction, compared to the conventional case where both the housings 2 and 4 are superposed only in the radial direction.
- the gear housing 2 can be further reduced in size.
- FIG. 6 shows a second embodiment of the present invention, in which only the structure of the second valve 69 is changed based on the first embodiment. Therefore, below, only a different part from 1st Embodiment is demonstrated, and the detailed description is abbreviate
- the second valve 69 is configured similarly to the first valve 18 according to the first embodiment. That is, unlike the first embodiment, the valve case 35 is not interposed, and the second valve housing hole 70 is formed in the bottom portion 2c itself.
- the second valve seat member 37 and the second valve seat hole 70 are directly formed in the second valve housing hole 70.
- a two-valve body 38 and the like are arranged, and the second valve housing hole 70 is sealed with a sealing plug 71 similar to the first valve 18.
- the same effect as that of the first embodiment can be obtained, and the valve case is formed by forming the second valve housing hole 70 in the bottom 2c itself. Since the number of parts can be reduced by omitting 35, the manufacturing cost of the apparatus can be reduced.
- FIG. 7 is an integral type power steering device 81 in which a first valve 18 is disposed on the peripheral wall of the sector gear housing 2b.
- the basic configuration is the same as that in FIG. 1, and thus the same reference numerals are given to the same configuration and the description thereof is omitted.
- the technical idea of the present invention in which the valve body is directly accommodated in the housing body can be applied.
- the manufacturing cost of the device can be reduced.
- FIG. 8 is a cross-sectional view of the integral type power steering device 1 of FIG. 1 cut at different angular positions in the circumferential direction.
- the integral type power steering device 1 is formed on the outer peripheral side of the fitting convex portion 4b in the valve housing 4.
- An air bleeder 90 that is disposed so as to open to a later-described depression 96 and that bleeds air from the first pressure chamber P1 is shown. Since other configurations are the same as those in FIG. 1, the same components are denoted by the same reference numerals and description thereof is omitted.
- the air brewer 90 is a ball type check valve, and includes a valve housing hole 91 formed in the valve housing 4 itself, and a substantially cylindrical shape screwed into the valve housing hole 91.
- a coil spring 95 that urges the valve seat 92a formed on the inner periphery of the intermediate portion in the axial direction.
- the operation of the air brewer 90 will be described.
- air (bubbles) mixed in the hydraulic oil in the pressure chambers P1 and P2 is recessed on the outer peripheral side of the upper end of the first pressure chamber P1. It will accumulate in the hollow part 96 made.
- the ball 93 is pushed up by the oil pressure, and the valve is opened. It is discharged to the reservoir tank.
- the present invention can also be applied to various check valves such as the air bleeder 90.
- the sealing member since the sealing member has both the sealing function of the first valve housing hole and the function as the seating surface of the coil spring, the number of parts can be reduced and the manufacturing cost of the device can be reduced. Contribute to.
- the sealing member is formed with a small-diameter portion inserted into the first valve housing hole, an outer diameter larger than the small-diameter portion, and disposed outside the first valve housing hole.
- An integral-type power steering device comprising: an exposed large-diameter portion, and the large-diameter portion having an engaging portion that can be engaged with the tool when the sealing member is attached by a tool. .
- the engaging portion with the tool that requires a predetermined size from the first valve housing hole and forming the portion to be housed in the first valve housing hole with a small diameter, The engagement portion with the tool can be secured while suppressing the increase in diameter of the first valve housing hole.
- the engaging portion with the tool is recessed in the outer end surface of the large-diameter portion of the sealing member, compared with the case where the engaging portion with the tool is formed on the outer periphery of the large-diameter portion, Interference with the steering shaft or the like can be suppressed, and assembly workability can be improved.
- the force acting on the first pin from the piston can be dispersed by bringing the substantially center of the tip surface of the first pin into contact with the piston. Thereby, the deformation of the first pin can be suppressed.
- the first valve body is formed on the valve seat member side with respect to the large-diameter portion that slides with the inner peripheral surface of the first valve housing hole, and has an outer diameter that is larger than that of the large-diameter portion.
- An integral type power steering device comprising a small-diameter portion set to be small.
- the hydraulic oil can be formed by the first valve body alone.
- the first valve body can be prevented from falling down while securing an oil passage through which the gas passes.
- the first valve body has a through hole into which one end side in the longitudinal direction of the first pin is press-fitted, The integral type power steering device, wherein the first pin is press-fitted and fixed in the through hole by pressing the other end in the longitudinal direction with the piston when the hydraulic power source is not operating. .
- the position adjustment work of the first pin can be performed easily and accurately.
- the first valve housing hole is formed with a reduced diameter at a large-diameter portion in which the first valve body is accommodated and an end portion of the large-diameter portion on the first pressure chamber side, and the first pin is inserted through the small-diameter portion.
- the first valve seat member is formed in a cylindrical shape, and one end side of the first valve seat member abuts on a stepped portion formed at the boundary between the large diameter portion and the small diameter portion. Integral type power steering device characterized by contact.
- the displacement of the valve seat member is suppressed as compared with the prior art in which the valve seat member is caulked and fixed to the valve body.
- the step portion between the large diameter portion and the small diameter portion of the first valve accommodating hole can be easily formed.
- the sealing member since the sealing member has both the sealing function of the first valve housing hole and the function as the seating surface of the coil spring, the number of parts can be reduced and the manufacturing cost of the device can be reduced. Contribute to.
- the sealing member is formed with a small-diameter portion inserted into the first valve housing hole, an outer diameter larger than the small-diameter portion, and disposed outside the first valve housing hole.
- An integral-type power steering device comprising: an exposed large-diameter portion, and the large-diameter portion having an engaging portion that can be engaged with the tool when the sealing member is attached by a tool. .
- the engaging portion with the tool that requires a predetermined size from the first valve housing hole and forming the portion to be housed in the first valve housing hole with a small diameter, The engagement portion with the tool can be secured while suppressing the increase in diameter of the first valve housing hole.
- the engaging portion with the tool is recessed in the outer end surface of the large-diameter portion of the sealing member, compared with the case where the engaging portion with the tool is formed on the outer periphery of the large-diameter portion, Interference with the steering shaft or the like can be suppressed, and assembly workability can be improved.
- the force acting on the first pin from the piston can be dispersed by bringing the substantially center of the tip surface of the first pin into contact with the piston. Thereby, the deformation of the first pin can be suppressed.
- the valve housing is provided with a fitting convex portion that protrudes toward the gear housing by reducing the diameter of the opposed end portion at the opposite end portion of the gear housing, and at the opening end portion of the gear housing.
- An integral type power steering apparatus wherein a fitting concave portion for receiving the fitting convex portion is provided by expanding the diameter of the opening end portion.
- the valve housing and the gear housing are superposed in the axial direction at the opening end of the gear housing, so that the valve housing and the gear housing are superposed only in the radial direction.
- the outer diameter of the gear housing can be reduced by the amount of the overlap in the axial direction.
- the gear housing can be further reduced in size.
- the first valve body is formed on the valve seat member side with respect to the large-diameter portion that slides with the inner peripheral surface of the first valve housing hole, and has an outer diameter that is larger than that of the large-diameter portion.
- An integral type power steering device comprising a small-diameter portion set to be small.
- the hydraulic oil can be formed by the first valve body alone.
- the first valve body can be prevented from falling down while securing an oil passage through which the gas passes.
- the first valve body has a through hole into which one end side in the longitudinal direction of the first pin is press-fitted, The integral type power steering device, wherein the first pin is press-fitted and fixed in the through hole by pressing the other end in the longitudinal direction with the piston when the hydraulic power source is not operating. .
- the position adjustment work of the first pin can be performed easily and accurately.
- SYMBOLS 1 Integral type power steering apparatus 2 ... Gear housing 2a ... Cylinder part 2d ... Fitting recessed part 3 ... Housing main body (housing) 4 ... Valve housing 4a ... Rotary valve housing (shaft insertion hole) 4b ... fitting convex part 5 ... steering wheel 6 ... ball screw mechanism (first conversion mechanism) 7 ... Piston 7a ... Rack gear (tooth part, second conversion mechanism) 8a ... Sector gear (second conversion mechanism) 9 ... Stub shaft (input shaft) DESCRIPTION OF SYMBOLS 17 ... Rotary valve 18 ... 1st valve 19 ... 2nd valve 21 ... 1st valve accommodation hole 21a ... Step part 22 ...
- Sealing plug (sealing member) 23 ... 1st valve body 24 ... 1st valve seat member (1st valve seat part) 25.
- First compression coil spring (first biasing member) 26 ... 1st pin (1st pin part) 27 ... 1st large diameter part (large diameter part) 28 ... 1st small diameter part (small diameter part) 32 ... Guide hole (first pin insertion hole) P1 ... 1st pressure chamber P2 ... 2nd pressure chamber
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Abstract
Description
以下、本発明に係るインテグラル型パワーステアリング装置の実施形態を、図面に基づいて説明する。なお、下記の各実施形態においても、従来と同様、当該インテグラル型パワーステアリング装置を自動車に適用した例を基に説明する。
〔第2実施形態〕
図6は、本発明の第2実施形態を示し、上記第1実施形態を基本構成として第2バルブ69の構造のみを変更したものである。よって、以下では第1実施形態と異なる部分についてのみ説明し、図1と共通する部分にはそれぞれ同一符号を付すことで、詳細な説明は省略する。
図7,8は本発明の一部の適用が想定される例を示している。
上記第1付勢部材としてのコイルスプリングは、軸方向一端側が上記封止部材と当接し、他端側が上記第1弁体と当接するように設けられることを特徴とするインテグラル型パワーステアリング装置。
上記封止部材は、上記第1バルブ収容孔内に挿入される小径部と、該小径部よりも外径が大きく形成され、且つ、上記第1バルブ収容孔の外側に配置されて、外部に露出する大径部と、から構成され、該大径部は、封止部材が工具により取り付けられる際に該工具と係合可能な係合部を有することを特徴とするインテグラル型パワーステアリング装置。
上記封止部材における工具との係合部は、上記封止部材の大径部外端面の径方向ほぼ中央に凹設されたことを特徴とするインテグラル型パワーステアリング装置。
上記第1ピンは、上記長手方向他端側の先端面のほぼ中心が上記ピストンと当接することを特徴とするインテグラル型パワーステアリング装置。
上記第1弁体は、上記第1バルブ収容孔の内周面と摺動する大径部と、該大径部よりも上記弁座部材側に形成され、該大径部よりも外径が小さく設定された小径部と、から構成されることを特徴とするインテグラル型パワーステアリング装置。
上記第1弁体は、上記第1ピンの長手方向一端側が圧入される貫通孔を有し、
上記第1ピンは、上記油圧源の非動作時において、上記長手方向他端側を上記ピストンで押圧することによって、該貫通孔内に圧入固定されることを特徴とするインテグラル型パワーステアリング装置。
上記第1バルブ収容孔は、上記第1弁体が収容される大径部と、該大径部の第1圧力室側の端部に縮径形成され、上記第1ピンが挿通する小径部と、から構成され、上記第1弁座部材は、筒状に形成されるとともに、該第1弁座部材の一端側が上記大径部と上記小径部との境界に形成される段部に当接することを特徴とするインテグラル型パワーステアリング装置。
上記第1バルブ収容孔は、上記大径部側から機械加工によって形成され、該大径部の外端部は封止部材によって封止されることを特徴とするインテグラル型パワーステアリング装置。
上記第1付勢部材としてのコイルスプリングは、軸方向一端側が上記封止部材と当接し、他端側が上記第1弁体と当接するように設けられることを特徴とするインテグラル型パワーステアリング装置。
上記封止部材は、上記第1バルブ収容孔内に挿入される小径部と、該小径部よりも外径が大きく形成され、且つ、上記第1バルブ収容孔の外側に配置されて、外部に露出する大径部と、から構成され、該大径部は、封止部材が工具により取り付けられる際に該工具と係合可能な係合部を有することを特徴とするインテグラル型パワーステアリング装置。
上記封止部材における工具との係合部は、上記封止部材の大径部外端面の径方向ほぼ中央に凹設されたことを特徴とするインテグラル型パワーステアリング装置。
上記第1ピンは、上記長手方向他端側の先端面のほぼ中心が上記ピストンと当接することを特徴とするインテグラル型パワーステアリング装置。
上記バルブハウジングの上記ギヤハウジングとの対向端部に、該対向端部を縮径することによって上記ギヤハウジング側に凸となる嵌合凸部が設けられると共に、上記ギヤハウジングの開口端部に、該開口端部を拡径することによって上記嵌合凸部を受容する嵌合凹部が設けられていることを特徴とするインテグラル型パワーステアリング装置。
上記第1弁体は、上記第1バルブ収容孔の内周面と摺動する大径部と、該大径部よりも上記弁座部材側に形成され、該大径部よりも外径が小さく設定された小径部と、から構成されることを特徴とするインテグラル型パワーステアリング装置。
上記第1弁体は、上記第1ピンの長手方向一端側が圧入される貫通孔を有し、
上記第1ピンは、上記油圧源の非動作時において、上記長手方向他端側を上記ピストンで押圧することによって、該貫通孔内に圧入固定されることを特徴とするインテグラル型パワーステアリング装置。
2…ギヤハウジング
2a…シリンダ部
2d…嵌合凹部
3…ハウジング本体(ハウジング)
4…バルブハウジング
4a…ロータリバルブ収容部(軸挿通孔)
4b…嵌合凸部
5…操舵輪
6…ボールねじ機構(第1変換機構)
7…ピストン
7a…ラックギヤ(歯部,第2変換機構)
8a…セクタギヤ(第2変換機構)
9…スタブシャフト(入力軸)
17…ロータリバルブ
18…第1バルブ
19…第2バルブ
21…第1バルブ収容孔
21a…段部
22…封止栓(封止部材)
23…第1弁体
24…第1弁座部材(第1弁座部)
25…第1圧縮コイルスプリング(第1付勢部材)
26…第1ピン(第1ピン部)
27…第1大径部(大径部)
28…第1小径部(小径部)
32…ガイド孔(第1ピン挿通孔)
P1…第1圧力室
P2…第2圧力室
Claims (20)
- 軸方向一端側が閉塞されると共に他端側が開口するように形成された金属材料からなるギヤハウジングと、該ギヤハウジングの上記他端側開口を閉塞するように設けられ、かつ、軸方向に沿って軸挿通孔が貫通形成された金属材料からなるバルブハウジングとから構成されるハウジングと、
一端側がステアリングホイールに連係され、他端側が上記バルブハウジングに挿通されることによって上記ギヤハウジングの内部に臨むように設けられた操舵軸と、
上記操舵軸の他端側に連係し、上記ギヤハウジングの内部を第1圧力室及び第2圧力室に隔成するピストンと、
上記操舵軸と上記ピストンとの間に設けられ、上記操舵軸の回転運動を上記ピストンの軸方向運動へと変換する第1変換機構と、
上記ピストンの外周に形成された歯部と歯合して上記ピストンの軸方向移動を回転運動へと変換することにより転舵を行う第2変換機構と、
上記軸挿通孔内において上記操舵軸と連係するように設けられ、上記操舵軸の回転方向に応じて外部の油圧源から供給される作動油を上記第1圧力室又は第2圧力室へと選択的に導くロータリバルブと、
上記バルブハウジングに設けられ、上記ピストンの移動によって上記第1圧力室の容積が許容最小量となる第1所定位置に上記ピストンが到達したときに上記第2圧力室内の油圧を上記第1圧力室側へと排出する第1バルブと、
上記ギヤハウジングに設けられ、上記ピストンの移動によって上記第2圧力室の容積が許容最小量となる第2所定位置に上記ピストンが到達したときに上記第1圧力室内の油圧を上記第2圧力室へと排出する第2バルブと、を備え、
少なくとも上記第1バルブは、
上記バルブハウジング自体を機械加工することによって形成された第1バルブ収容孔と、
上記第1バルブ収容孔において上記第1圧力室側に設けられ、その内周側に軸方向に沿って第1ピン挿通孔が貫通形成された第1弁座部と、
上記第1バルブ収容孔内において上記第1弁座部と対向するかたちで軸方向移動可能に設けられ、上記第1弁座部に着座することによって上記第2圧力室側から上記第1圧力室側への作動油の移動を遮断する第1弁体と、
上記第1弁体と一体的に構成され、上記第1ピン挿通孔を通じて上記第1圧力室内へと臨み、上記ピストンの上記第1所定位置への到達時に上記ピストンによって押圧されることで上記第1弁体に移動力を付与する第1ピン部と、
上記第1弁体を上記弁座部材側へ付勢する第1付勢部材と、から構成されることを特徴とするインテグラル型パワーステアリング装置。 - 請求項1に記載のインテグラル型パワーステアリング装置において、
上記第1バルブ収容孔は、上記第1弁体が収容される大径部と、該大径孔の第1圧力室側の端部に縮径形成され、上記第1ピンが挿通する小径部と、から構成され、
上記第1弁座部材は、筒状に形成されるとともに、該第1弁座部材の一端側が上記大径部と上記小径部との境界に形成される段部に当接することを特徴とするインテグラル型パワーステアリング装置。 - 請求項2に記載のインテグラル型パワーステアリング装置において、
上記第1バルブ収容孔は、上記大径部側から機械加工によって形成され、
該大径部の外端部は、封止部材によって封止されることを特徴とするインテグラル型パワーステアリング装置。 - 請求項3に記載のインテグラル型パワーステアリング装置において、
上記第1付勢部材としてのコイルスプリングは、軸方向一端側が上記封止部材と当接し、他端側が上記第1弁体と当接するように設けられることを特徴とするインテグラル型パワーステアリング装置。
この発明によれば、封止部材が第1バルブ収容孔の封止機能とコイルスプリングの着座面としての機能を兼ねることから、部品点数の削減を図ることができ、装置の製造コストの低廉化に寄与する。 - 請求項4に記載のインテグラル型パワーステアリング装置において、
上記封止部材は、上記第1バルブ収容孔内に挿入される小径部と、該小径部よりも外径が大きく形成され、且つ、上記第1バルブ収容孔の外側に配置されて、外部に露出する大径部と、から構成され、該大径部は、封止部材が工具により取り付けられる際に該工具と係合可能な係合部を有することを特徴とするインテグラル型パワーステアリング装置。 - 請求項5に記載のインテグラル型パワーステアリング装置において、
上記封止部材における工具との係合部は、上記封止部材の大径部外端面の径方向ほぼ中央に凹設されたことを特徴とするインテグラル型パワーステアリング装置。 - 請求項1に記載のインテグラル型パワーステアリング装置において、
上記第1ピンは、上記長手方向他端側の先端面のほぼ中心が上記ピストンと当接することを特徴とするインテグラル型パワーステアリング装置。 - 請求項1に記載のインテグラル型パワーステアリング装置において、
上記バルブハウジングの上記ギヤハウジングとの対向端部に、該対向端部を縮径することによって上記ギヤハウジング側に凸となる嵌合凸部が設けられると共に、
上記ギヤハウジングの開口端部に、該開口端部を拡径することによって上記嵌合凸部を受容する嵌合凹部が設けられていることを特徴とするインテグラル型パワーステアリング装置。 - 請求項1に記載のインテグラル型パワーステアリング装置において、
上記第1弁体は、上記第1バルブ収容孔の内周面と摺動する大径部と、該大径部よりも上記弁座部材側に形成され、該大径部よりも外径が小さく設定された小径部と、から構成されることを特徴とするインテグラル型パワーステアリング装置。 - 請求項1に記載のインテグラル型パワーステアリング装置において、
上記第1弁体は、上記第1ピンの長手方向一端側が圧入される貫通孔を有し、
上記第1ピンは、上記油圧源の非動作時において、上記長手方向他端側を上記ピストンで押圧することによって、該貫通孔内に圧入固定されることを特徴とするインテグラル型パワーステアリング装置。 - 軸方向一端側が閉塞されると共に他端側が開口するように形成された金属材料からなるギヤハウジングと、該ギヤハウジングの上記他端側開口を閉塞するように設けられ、かつ、軸方向に沿って軸挿通孔が貫通形成された金属材料からなるバルブハウジングとから構成されるハウジングと、
一端側がステアリングホイールに連係され、他端側が上記バルブハウジングに挿通されることによって上記ギヤハウジングの内部に臨むように設けられた操舵軸と、
上記操舵軸の他端側に連係し、上記ギヤハウジングの内部を第1圧力室及び第2圧力室に隔成するピストンと、
上記操舵軸と上記ピストンとの間に設けられ、上記操舵軸の回転運動を上記ピストンの軸方向運動へと変換する第1変換機構と、
上記ピストンの外周に形成された歯部と歯合して上記ピストンの軸方向移動を回転運動へと変換することにより転舵を行う第2変換機構と、
上記軸挿通孔内において上記操舵軸と連係するように設けられ、上記操舵軸の回転方向に応じて外部の油圧源から供給される作動油を上記第1圧力室又は第2圧力室へと選択的に導くロータリバルブと、
上記バルブハウジングに設けられ、上記ピストンの移動によって上記第1圧力室の容積が許容最小量となる第1所定位置に上記ピストンが到達したときに上記第2圧力室内の油圧を上記第1圧力室側へと排出する第1バルブと、
上記ギヤハウジングに設けられ、上記ピストンの移動によって上記第2圧力室の容積が許容最小量となる第2所定位置に上記ピストンが到達したときに上記第1圧力室内の油圧を上記第2圧力室へと排出する第2バルブと、を備え、
少なくとも上記第1バルブは、
上記バルブハウジングに設けられ、上記ピストンの移動方向とほぼ一致するように構成された第1バルブ収容孔と、
上記第1バルブ収容孔において上記第1圧力室側に設けられ、その内周側に軸方向に沿って第1ピン挿通孔が貫通形成された第1弁座部と、
上記第1バルブ収容孔内において上記第1弁座部と対向するかたちで軸方向移動可能に設けられ、上記第1弁座部に着座することによって上記第2圧力室側から上記第1圧力室側への作動油の移動を遮断する第1弁体と、
上記第1弁体と一体的に構成され、上記第1ピン挿通孔を通じて上記第1圧力室内へと臨み、上記ピストンの上記第1所定位置への到達時に上記ピストンによって押圧されることで上記第1弁体に移動力を付与する第1ピン部と、
上記第1弁体を上記弁座部材側へ付勢する第1付勢部材と、から構成されることを特徴とするインテグラル型パワーステアリング装置。 - 請求項11に記載のインテグラル型パワーステアリング装置において、
上記第1バルブ収容孔は、上記第1弁体が収容される大径部と、該大径部の第1圧力室側の端部に縮径形成され、上記第1ピンが挿通する小径部と、から構成され、
上記第1弁座部材は、筒状に形成されるとともに、該第1弁座部材の一端側が上記大径部と上記小径部との境界に形成される段部に当接することを特徴とするインテグラル型パワーステアリング装置。 - 請求項12に記載のインテグラル型パワーステアリング装置において、
上記第1バルブ収容孔は、上記大径部側から機械加工によって形成され、該大径部の外端部は封止部材によって封止されることを特徴とするインテグラル型パワーステアリング装置。 - 請求項13に記載のインテグラル型パワーステアリング装置において、
上記第1付勢部材としてのコイルスプリングは、軸方向一端側が上記封止部材と当接し、他端側が上記第1弁体と当接するように設けられることを特徴とするインテグラル型パワーステアリング装置。 - 請求項14に記載のインテグラル型パワーステアリング装置において、
上記封止部材は、上記第1バルブ収容孔内に挿入される小径部と、該小径部よりも外径が大きく形成され、且つ、上記第1バルブ収容孔の外側に配置されて、外部に露出する大径部と、から構成され、該大径部は、封止部材が工具により取り付けられる際に該工具と係合可能な係合部を有することを特徴とするインテグラル型パワーステアリング装置。 - 請求項15に記載のインテグラル型パワーステアリング装置において、
上記封止部材における工具との係合部は、上記封止部材の大径部外端面の径方向ほぼ中央に凹設されたことを特徴とするインテグラル型パワーステアリング装置。 - 請求項11に記載のインテグラル型パワーステアリング装置において、
上記第1ピンは、上記長手方向他端側の先端面のほぼ中心が上記ピストンと当接することを特徴とするインテグラル型パワーステアリング装置。 - 請求項11に記載のインテグラル型パワーステアリング装置において、
上記バルブハウジングの上記ギヤハウジングとの対向端部に、該対向端部を縮径することによって上記ギヤハウジング側に凸となる嵌合凸部が設けられると共に、上記ギヤハウジングの開口端部に、該開口端部を拡径することによって上記嵌合凸部を受容する嵌合凹部が設けられていることを特徴とするインテグラル型パワーステアリング装置。 - 請求項11に記載のインテグラル型パワーステアリング装置において、
上記第1弁体は、上記第1バルブ収容孔の内周面と摺動する大径部と、該大径部よりも上記弁座部材側に形成され、該大径部よりも外径が小さく設定された小径部と、から構成されることを特徴とするインテグラル型パワーステアリング装置。 - 請求項11に記載のインテグラル型パワーステアリング装置において、
上記第1弁体は、上記第1ピンの長手方向一端側が圧入される貫通孔を有し、
上記第1ピンは、上記油圧源の非動作時において、上記長手方向他端側を上記ピストンで押圧することによって、該貫通孔内に圧入固定されることを特徴とするインテグラル型パワーステアリング装置。
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CN201380070115.1A CN104918840B (zh) | 2013-01-23 | 2013-12-27 | 整体型动力转向装置 |
DE112013006484.7T DE112013006484T5 (de) | 2013-01-23 | 2013-12-27 | Integrierte Servolenkvorrichtung |
US14/760,124 US9511797B2 (en) | 2013-01-23 | 2013-12-27 | Integral power steering device |
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JPS5621971A (en) * | 1979-07-27 | 1981-02-28 | Zahnradfabrik Friedrichshafen | Servo control device |
US5419235A (en) * | 1994-02-28 | 1995-05-30 | Trw Inc. | Power steering gear assembly |
JP2005022636A (ja) * | 2003-06-09 | 2005-01-27 | Unisia Jkc Steering System Co Ltd | インテグラル型パワーステアリング装置 |
JP2012201139A (ja) * | 2011-03-24 | 2012-10-22 | Hitachi Automotive Systems Steering Ltd | インテグラル型パワーステアリング装置 |
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US3896703A (en) * | 1974-06-24 | 1975-07-29 | Powersteering Trust Reg | Arrangement for relieving the mechanical stresses in power assisted steering for vehicles in the full-lock steering positions |
US4293673A (en) * | 1978-12-28 | 1981-10-06 | Union Carbide Corporation | Spheroidal polymerization catalyst, process for preparing, and use for ethylene polymerization |
US4942803A (en) * | 1987-07-15 | 1990-07-24 | Trw Inc. | Steering gear with pressure-balanced valve |
DE10203384B9 (de) * | 2002-01-29 | 2007-01-18 | Trw Fahrwerksysteme Gmbh & Co Kg | Servolenksystem |
US7819217B2 (en) * | 2005-12-23 | 2010-10-26 | Hitachi, Ltd. | Power steering apparatus, method of controlling the same and method of assembling the same |
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Publication number | Priority date | Publication date | Assignee | Title |
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JPS5621971A (en) * | 1979-07-27 | 1981-02-28 | Zahnradfabrik Friedrichshafen | Servo control device |
US5419235A (en) * | 1994-02-28 | 1995-05-30 | Trw Inc. | Power steering gear assembly |
JP2005022636A (ja) * | 2003-06-09 | 2005-01-27 | Unisia Jkc Steering System Co Ltd | インテグラル型パワーステアリング装置 |
JP2012201139A (ja) * | 2011-03-24 | 2012-10-22 | Hitachi Automotive Systems Steering Ltd | インテグラル型パワーステアリング装置 |
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