WO2001098131A1 - Dispositif de direction des roues arrieres - Google Patents
Dispositif de direction des roues arrieres Download PDFInfo
- Publication number
- WO2001098131A1 WO2001098131A1 PCT/JP2000/004111 JP0004111W WO0198131A1 WO 2001098131 A1 WO2001098131 A1 WO 2001098131A1 JP 0004111 W JP0004111 W JP 0004111W WO 0198131 A1 WO0198131 A1 WO 0198131A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- steering
- front wheel
- wheel
- shaft
- rear front
- Prior art date
Links
- 230000007246 mechanism Effects 0.000 claims abstract description 26
- 230000005540 biological transmission Effects 0.000 claims description 8
- 230000007423 decrease Effects 0.000 claims description 6
- 230000007935 neutral effect Effects 0.000 claims description 4
- 239000000725 suspension Substances 0.000 description 6
- 230000008859 change Effects 0.000 description 5
- 238000001514 detection method Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000006872 improvement Effects 0.000 description 3
- 241001634822 Biston Species 0.000 description 2
- FFGPTBGBLSHEPO-UHFFFAOYSA-N carbamazepine Chemical compound C1=CC2=CC=CC=C2N(C(=O)N)C2=CC=CC=C21 FFGPTBGBLSHEPO-UHFFFAOYSA-N 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 238000012856 packing Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000004043 responsiveness Effects 0.000 description 2
- 230000002542 deteriorative effect Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D7/00—Steering linkage; Stub axles or their mountings
- B62D7/06—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins
- B62D7/14—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering
- B62D7/142—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering specially adapted for particular vehicles, e.g. tractors, carts, earth-moving vehicles, trucks
- B62D7/144—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering specially adapted for particular vehicles, e.g. tractors, carts, earth-moving vehicles, trucks for vehicles with more than two axles
Definitions
- the present invention relates to a rear wheel steering device for a vehicle, and more particularly to a rear wheel steering device for a rear two-axle vehicle that supports a rear portion of a vehicle body with a rear front shaft and a rear rear shaft.
- Trucks with a large maximum load capacity cannot support most of the loaded load with a single rear axle, so trucks with two rear axles are more widely used than before.
- the load imbalance between the rear front shaft and the rear shaft is eliminated, and both shafts can receive the load stably.
- a truck configured to suspend the rear two shafts by a trunnion type suspension device, receive the full load of the rear two shafts at the intermediate position between the rear front shaft and the rear rear shaft, that is, the mounting position of the trunnion bracket. become. Therefore, even with the two rear axes, the load is received at one point in the longitudinal direction of the vehicle, and a large load is supported at this position.
- the rear front wheel is also sensitively steered in response to the fine steering of the front wheel, the rear front wheel steering mechanism operates more frequently, so that the rear front wheel steering mechanism is easily worn, and the durability of the steering mechanism is increased. And the reliability of the vehicle decreases. Further, if the rear front wheels are steered sensitively in response to fine steering of the front wheels, the straightness of the vehicle during high-speed running may be impaired, and running stability during high-speed running may be reduced.
- the first object of the present invention is to reduce the load on the front wheels by supporting most of the load on the two rear axles, and to reduce uneven wear of the rear front wheels by enabling the rear front wheels to be steered. It is an object of the present invention to provide a rear-wheel steering device that can prevent the rear-wheel steering.
- a second object of the present invention is to enable the rear front wheel to be steered by a relatively small actuator, to prevent a reduction in durability of the rear front wheel due to unnecessary steering of the rear front wheel, and to further increase the speed.
- An object of the present invention is to provide a rear-wheel steering device that can improve straight-line traveling performance and improve running stability. Disclosure of the invention
- the invention according to claim 1 is an improvement of a rear wheel steering device of a vehicle in which a rear portion of a vehicle body is supported by a rear front shaft 18 and a rear rear shaft 20 as shown in FIGS. 1 to 3 and 8. o
- Its characteristic configuration is that it drives a front-rear wheel steering mechanism that is capable of steering left and right rear front wheels 17, 17 rotatably attached to both ends of the rear-front shaft 18, and a rear-front wheel steering mechanism.
- the rear front wheels 18 are steered by an Control means 69 for controlling the Yue night 5 1, the control means 69 stops the steering of the rear front wheel 18 when the vehicle speed is almost 0, and the front wheel 15 even when the vehicle speed is almost 0.
- the control means 69 is configured to operate the actuator 51 when the difference between the theoretical steering angle of the rear front wheel 17 and the actual steering angle with respect to the steering angle exceeds a predetermined value.
- control means 69 may be configured to deactivate the actuator 51 when the transmission 25 is in the neutral position. Further, the control means 69 may be configured to deactivate the actuator 51 when the clutch is in the cutoff state.
- the invention according to claim 4 is an improvement of a rear wheel steering device of a vehicle in which a rear portion of a vehicle body is supported by a rear front shaft 18 and a rear rear shaft 20 as shown in FIGS. 1 to 3 and 8. .
- Its characteristic configuration is that it drives the rear-front wheel steering mechanism, which is rotatably mounted on both ends of the rear-front axle 18 and can steer the left and right rear front wheels 17 and 17, and drives this rear-front wheel steering mechanism. It comprises an actuator 51 for steering the rear front wheel 17 and a control means 69 for controlling the actuator 51, and the control means 69 controls the actuator 51 according to the steering angle of the front wheel 15. When the steering angle of the front wheel 15 is smaller than a predetermined value, the control means 69 deactivates the actuator 51 to prevent the rear front wheel 17 from being steered. Where it was.
- the ratio of the steering angle of the rear front wheel 17 to the steering angle of the front wheel 15 may be changed according to the vehicle speed, and the ratio of the steering angle of the rear front wheel 17 may decrease as the vehicle speed increases. Further, the limit value of the steering angle of the front wheel 15 that does not steer the rear front wheel 17 may be changed according to the vehicle speed.
- the invention according to claim 7 has a front portion of a vehicle body supported by a front shaft 16 and a rear portion of the vehicle body having a rear front shaft 18 and a rear rear shaft 20.
- This is an improvement of the rear-wheel steering system for a vehicle consisting of a three-axle vehicle supported by a vehicle. Its characteristic configuration is that the center distance B between the rear front shaft 18 and the rear rear shaft 20 is set to more than 160 mm, and the rear front wheel 17 can be steered to the rear front shaft 18 And the front rear wheel 17 is steered when the vehicle turns. There is.
- the rear / front shaft 18 may be a dead shaft or a driven shaft, and the rear shaft 20 may be a drive shaft.
- Both the front and rear wheels 17 and 19 may be double wheels o
- the inter-axis distance B between the rear front shaft 18 supporting the rear part of the vehicle body and the rear shaft 20 is set to 160 mm or more, more preferably 180 mm or more,
- the distance B between the front front shaft 18 and the rear shaft 20 is 20% or more, more preferably 25%, with respect to the center distance A between the front shaft 16 and the rear shaft 18.
- the rear front axis 18 and the rear rear axis 20 are arranged so that they are separated by more than%. If this ratio is less than 20%, the load on the front shaft 16 cannot be reduced sufficiently.
- the rear shaft 20 is a drive shaft having rear wheels 19 that are non-steerably mounted on both ends thereof.
- the rear front shaft 18 is a driven shaft having rear front wheels 17 that are steerably mounted on both sides thereof. Further, the rear front wheel 17 is configured to be steered via the electronic control unit 69 and the actuator 51 according to the steering angle of the front wheel 15.
- Such electronic steering of the front and rear wheels 17 is not performed when the vehicle speed is almost 0, so that the front and rear wheels 17 can be steered even with a relatively small-sized and small-output actuator 51.
- the vehicle speed is 0, if the difference between the theoretical steering angle of the rear front wheel 17 and the actual steering angle of the rear wheel 17 with respect to the steering angle of the front wheel 15 is larger than a certain angle, By operating the vehicle, the rear front wheel 17 can be smoothly steered when the vehicle starts moving.
- the steering of the rear front wheel 17 during running is performed in conjunction with the steering angle of the front wheel 15 and the ratio of the steering angle of the rear front wheel 17 to the steering angle of the front wheel 15 changes according to the vehicle speed. That is, as the vehicle speed increases, the ratio of the steering angle of the rear front wheel 17 to the front wheel 15 is reduced.
- the steering angle of the front wheels 15 is equal to or smaller than a predetermined value, the steering of the rear front wheels 17 is stopped, that is, a dead zone is provided to stop unnecessary steering of the rear front wheels 17.
- the limit value of the steering angle in the dead zone of the front wheel 15 where the rear front wheel 17 is stopped in accordance with the vehicle speed the straightness during high-speed running is improved and the running stability is improved. ing. BRIEF DESCRIPTION OF THE FIGURES
- FIG. 1 is a side view of a truck provided with the rear wheel steering device of the present invention.
- FIG. 2 is a plan view showing the arrangement of wheels when the truck turns.
- FIG. 3 is a plan view showing the overall arrangement of the track.
- FIG. 4 is a side view showing the suspension mechanism of the rear front shaft and the rear rear shaft.
- FIG. 5 is a longitudinal sectional view of a main part showing a mounting structure of the rear front wheel to the rear front shaft.
- FIG. 6 is an enlarged vertical sectional view of a main part of FIG.
- FIG. 7 is an enlarged plan view of a main part showing a mounting structure of the rear front wheel to the rear front shaft.
- FIG. 8 is a hydraulic circuit configuration diagram for operating a hydraulic cylinder that steers the rear front shaft.
- FIG. 9 is a flowchart showing the switching operation of the control valve.
- FIG. 10 is a flowchart showing control of the steering angle of the rear front wheel.
- FIG. 11 is a diagram showing a change in the steering angle of the rear front wheel with respect to a change in the steering angle of the front wheel.
- FIG. 12 is a diagram showing a change in the angle of the dead zone of the front wheels according to the vehicle speed.
- FIG. 13 is a diagram showing a change in the ratio of the steering angle of the front front wheels to the front wheels according to the vehicle speed.
- FIG. 1 shows a rear two-axle truck according to an embodiment of the present invention, and a cabinet 11 is mounted on a front portion of a body frame 10.
- a packing box 12 is mounted on the body frame 10 on the rear side of the cap 11.
- the front portion of the body frame 10 of such a truck is supported by a front shaft 16 having front wheels 15 rotatably mounted on both ends.
- the rear of the body frame 10 has a rear front shaft 18 on the left and right with a rear front wheel 17 rotatably mounted, and a rear rear shaft 20 on the left and right with a rear rear wheel 19 rotatably mounted.
- the front wheel 15 is a single wheel, and the rear front wheel 17 and the rear rear wheel 19 are double wheels.
- the arrangement of the front wheel 15, rear front wheel 17 and rear wheel 19 is configured as shown in Fig. 2.
- the rear front wheels 17 are steered in conjunction therewith, and the extension of the center axis of the rear front wheels 17 during turning is provided. Later, the intersection with the extension of the axis 20 is configured to coincide with the turning center of the vehicle. With this configuration, it is possible to reliably prevent the rear front shaft 17 from unevenly wearing the rear front shaft 17 while making the rear front shaft 18 largely eccentric to the rear shaft 20 forward of the conventional truck. Like that.
- the distance A between the front axis 16 and the rear axis 20 shown in Fig. 3 is set to 700 mm here, while the distance B between the rear front axis 18 and the rear axis 20 is B Is set to 1800 mm.
- the value of B is set to a value of about 130 mm. That is, the inter-axis distance B of the present embodiment is set to about 1.5 times the conventional inter-axis distance B.
- a load of 5 tons is applied to the front shaft 16, 10 tons to the rear front shaft 18, and 10 tons to the rear shaft 20.
- the relationship of such load distribution is a value proportional to the number of tires of each wheel 15, 17, 19. That is, a load of 2.5 tons is applied to each tire, so that the load applied to all the tires of the front wheel 15, the rear front wheel 17 and the rear rear wheel 19 becomes equal.
- the rear shaft 20 is a drive shaft
- the rear front shaft 18 is a dead shaft or a driven shaft.
- a differential gear device 23 is attached to the rear shaft 20 as shown in FIG. 3, and the differential gear device 23 and the engine 24 on the lower side of the cabinet 11 are connected to the transmission 2. 5 and a propeller shaft 26, so that the driving force from the engine 24 is transmitted to the wheels 19 later.
- trunnion bracket 77 is mounted on the frame 10 at a position almost halfway between the rear and front shafts 18 and the rear and rear shafts 20 as shown in detail in Fig. 7, and the trunnion bracket 77 rotates the trunnion shaft 78. Supported as possible. Further, trunnion seats 9 are respectively attached to both sides of the trunnion shaft 78, and a leaf spring 40 or a beam extending in the front-rear direction is attached to the trunnion sheet 79 via U-bolts.
- a front air spring 80 is interposed between the leaf spring 40 or the front end of the beam and the frame 10, and a rear air spring is provided between the leaf spring 40 or the rear end of the beam and the body frame 10.
- An air spring 81 is interposed.
- a rear front shaft 18 is suspended near the front end of the leaf spring 40, and a rear shaft 20 is suspended near the rear end of the leaf spring 40.
- the rear front shaft 18 is formed by an Elliott-type axle, and mounting arms 29 and 30 are provided on the right and left ends thereof, respectively, above and below.
- the upper and lower ends of the king pin 31 are held by the mounting arms 29, 30 respectively, and the center of the knuckle 32 is steerably mounted at an intermediate position in the length direction of the king pin 31.
- a hollow spindle 33 is fixed to one end of the knuckle 32, and a haptic 34 is rotatably attached to the spindle 33 via a bearing 36.
- a wheel 35 is attached to the hap 34, and a rear front wheel 17 is constituted by a tire attached to the outer peripheral surface of the wheel 35.
- the rear front axle 18 is formed with through-portions 39 which are respectively opened near the left and right ends thereof, and the through-portions 39 constitute suspension springs.
- the leaf spring 40 is inserted.
- the rear front shaft 18 is connected to the vehicle body frame 10 by a torque load.
- left and right knuckle arms 47 are respectively fixed to the left and right knuckles 32 that support the rear front wheel 17, and these knuckle arms 47 are mutually connected via tie rods 48. Be linked. This constitutes an Akkaman-type steering mechanism.
- a drag link 49 is connected to the other end of the knuckle arm 47 as shown in FIGS. 6 and 7, and the drag link 49 is connected to the hydraulic lever via the reversing lever 50 as shown in FIG. It is connected to the piston load of cylinder 51.
- a steering wheel 55 for steering the front wheels 15 is attached to an upper end of a steering shaft 56, and a lower end of the steering shaft 56 is connected to a steering shaft of a power steering device 57.
- a portman arm 58 is attached to the side of the power steering device 57, and a drag link 59 for steering the front wheel 15 is connected to the portman arm 58.
- An oil pump 62 is provided to drive the power steering device 57, and the oil pump 62 is directly connected to the engine 24. The oil pump 62 is configured to suck oil from the reservoir 63 and pressurize the oil.
- a relief valve 64 is connected to the oil pump 62, and an adjustment valve 65 constituting a priority valve is connected to a discharge side of the oil pump 62.
- the discharge side of the oil pump 62 is connected to a power steering device 57 through the regulating valve 65.
- a relief valve 66 is connected in parallel to a pipeline connecting the regulating valve 65 and the power steering device 57.
- a port on the side of the priority valve 65 is connected to a control valve 67, and the control valve 67 is connected to a pair of ports of the hydraulic cylinder 51 through a pair of pipes. Further, a cutoff valve 68 that cuts off or communicates a pair of ports of the hydraulic cylinder 51 is connected to a pair of pipelines connected to the pair of ports of the hydraulic cylinder 51. Further, both the priority valve 65 and the cutoff valve 68 are configured to be controlled by an electronic control unit (ECU) 69.
- ECU electronice control unit
- the control input of the electronic control unit 69 includes the transmission 2 of this vehicle.
- the detection outputs of the shift switch, brake switch, clutch switch and vehicle speed sensor are connected.
- Each detection output of 2 is also connected to the control input of the electronic control unit 69.
- the power steering device 57 is actuated via the steering shaft 56, the pitman arm 58 is rotated, and the front wheel is moved via the drag link 59. 15 is steered.
- the steering angle of the front wheels 15 at this time is detected by the steering angle sensor 71 and input to the electronic control unit 69.
- the priority valve 65 for supplying pressure oil to the power steering device 57 supplies excess oil to the control valve 67 side. If the control valve 67 has not been switched yet, the oil supplied to the control valve 67 via the priority valve 65 returns from the control valve 67 to the reservoir 63.
- the control valve 67 is switched by the electronic control unit 69, the oil supplied through the priority valve 65 is supplied to the hydraulic cylinder 51 through the control valve 67.
- the operating direction of the hydraulic cylinder 51 is one of a direction in which the biston rod is pulled in and a direction in which the biston rod is pushed out according to the switching direction of the control valve 67.
- the steering angle of the rear front wheel 17 is detected by a steering angle sensor 72 attached to the support shaft of the reversing lever 50, and when the steering angle reaches the steering angle corresponding to the steering angle of the front wheel 15, electronic control is performed.
- the device 69 switches the control valve 67 to the shut-off state, and stops the operation of the hydraulic cylinder 51. In this way, the rear front wheel 17 is steered at an angle linked to the steering angle of the front wheel 15. This state is shown in FIG.
- the above control operation is not performed when the vehicle speed is 0, as shown in detail in FIG.
- the electronic control unit 69 switches the control valve 67 to change the hydraulic pressure. Operate cylinder 51.
- the electronic control unit 69 reads the steering angle of the front wheels 15 based on the detection output of the steering angle sensor 71, reads the vehicle speed based on the detection output of the vehicle speed sensor, and calculates the dead zone shown in FIG. 11 from these values. That is, since the dead zone changes in accordance with the vehicle speed as shown in FIG. 12, the electronic control unit 69 calculates whether or not the steering angle of the front wheels 15 at that vehicle speed exceeds the angle of the dead zone. Then, it is determined whether or not the steering of the rear front wheel 17 is stopped.
- the electronic control unit 69 calculates the steering angles of the rear front wheels 17. As shown in FIG. 13, the ratio of the steering angle of the rear front wheel 17 to the steering angle of the front wheel 15 varies according to the vehicle speed. Accordingly, the transmission control device 69 reads the vehicle speed and calculates the steering angle of the rear front wheel 17 from the steering angle of the front wheel 15 at that time. Thereafter, the electronic control unit 69 switches the control valve 67 to determine whether or not the actual steering angle exceeds the target steering angle obtained by the above calculation. To shut off the control operation.
- the steering angle of the front wheels 15 becomes relatively smaller as the vehicle speed increases. For this reason, if the dead zone is kept constant, the responsiveness of the steering mechanism of the rear front wheel 17 gradually deteriorates as the speed increases.
- the dead zone is changed according to the vehicle speed as shown in Fig. 12 and the angle of the dead zone is gradually reduced as the vehicle speed increases, thereby preventing the sensitivity of the steering mechanism of the rear front wheels 17 from deteriorating.
- the ratio of the steering angle of the rear front wheel 17 to the steering angle of the front wheel 15 is changed according to the vehicle speed.
- the relative steering angle of the rear front wheel 17 increases. Unnecessary steering of the rear front wheel 17 is controlled especially during high-speed driving, so that the vehicle's straightness during high-speed driving can be improved and running stability can be improved. .
- the rear portion of the vehicle body is supported by the rear front axle and the rear rear axle, and the control means steers the rear front wheel through the actuating mechanism and the rear front wheel steering mechanism. Since the control means is configured to stop the steering of the rear front wheel when the vehicle speed is almost zero, the rear front wheel can be steered even in a small factory. Even if the vehicle speed is almost 0, if the difference between the theoretical steering angle of the front rear wheel and the actual steering angle with respect to the steering angle of the front wheels exceeds a predetermined value, the control means activates the actuator, so that the vehicle travels. The front front wheel can be steered smoothly when starting.
- control means deactivates the actuator when the transmission is in the neutral position or the clutch is in the disengaged state, Even if the difference between the theoretical steering angle of the front rear wheel and the actual steering angle with respect to the steering angle of the wheel exceeds a predetermined value, the actuator is not activated.
- control means controls the actuator so that the rear front wheel is steered according to the steering angle of the front wheel.
- the control means controls the actuator so as not to steer the rear front wheel.
- the steering angle of the rear front wheels increases as the vehicle speed increases. Is relatively small, and running stability during high-speed running can be improved.
- the limit value of the steering angle of the front wheels that do not perform steering of the rear front wheels is changed according to the vehicle speed, a dead zone corresponding to the vehicle speed is set, and the responsiveness of the steering of the rear front wheels during high-speed driving decreases. Can be improved.
- the distance between the rear front shaft and the rear rear shaft is set to be more than 160 mm.
- the rear front wheel is mounted on the rear front axle so as to be steerable and the rear front wheel is steered when the vehicle turns, the load sharing of each wheel of the three-axle vehicle can be made substantially equal.
- the rear front shaft is a dead shaft or a driven shaft and the rear shaft is a drive shaft
- a simple structure can be used for the rear front wheel steering mechanism and the rear rear wheel drive mechanism attached to the rear front shaft. it can.
- both the rear front wheel and the rear rear wheel are formed as a double wheel, the rear front wheel of the double wheel is steered, so that uneven wear of the rear front wheel and the rear rear wheel tire can be prevented.
- the rear wheel steering device of the present invention includes a rear two-axle vehicle that supports the rear side of the vehicle body by a rear front shaft and a rear rear shaft, a rear axle that supports the front end side of the vehicle body by a front shaft, and the rear side of the vehicle body by a rear front shaft and a rear side.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)
- Steering Control In Accordance With Driving Conditions (AREA)
Description
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Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP37054498A JP3759681B2 (ja) | 1998-12-25 | 1998-12-25 | åŸèŒªæèµè£ 眮 |
US10/049,554 US6763906B1 (en) | 1998-12-25 | 2000-06-22 | Rear wheel steering device |
PCT/JP2000/004111 WO2001098131A1 (fr) | 1998-12-25 | 2000-06-22 | Dispositif de direction des roues arrieres |
DE10084902T DE10084902T1 (de) | 2000-06-22 | 2000-06-22 | Hinterradlenkvorrichtung |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP37054498A JP3759681B2 (ja) | 1998-12-25 | 1998-12-25 | åŸèŒªæèµè£ 眮 |
PCT/JP2000/004111 WO2001098131A1 (fr) | 1998-12-25 | 2000-06-22 | Dispositif de direction des roues arrieres |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2001098131A1 true WO2001098131A1 (fr) | 2001-12-27 |
Family
ID=26344911
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2000/004111 WO2001098131A1 (fr) | 1998-12-25 | 2000-06-22 | Dispositif de direction des roues arrieres |
Country Status (3)
Country | Link |
---|---|
US (1) | US6763906B1 (ja) |
JP (1) | JP3759681B2 (ja) |
WO (1) | WO2001098131A1 (ja) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20060237242A1 (en) * | 2000-09-25 | 2006-10-26 | Burke Robert J | Lightweight surface vehicle |
CA2532015C (fr) * | 2003-07-17 | 2012-07-03 | Michelin Recherche Et Technique S.A. | Vehicule lourd |
FR2857649A1 (fr) * | 2003-07-17 | 2005-01-21 | Michelin Soc Tech | Vehicule lourd |
ATE510749T1 (de) * | 2008-06-24 | 2011-06-15 | Astra Veicoli Ind S P A | Lenksystem, insbesondere fÃŒr nutzfahrzeuge mit mehreren lenkachsen |
SE541383C2 (en) | 2015-06-11 | 2019-09-10 | Scania Cv Ab | A method and a system for steering a vehicle |
US10239371B2 (en) | 2015-11-11 | 2019-03-26 | Dana Heavy Vehicle Systems Group, Llc | Lightweight pusher/tag axle |
JP6711196B2 (ja) * | 2016-08-02 | 2020-06-17 | ãããèªåè»æ ªåŒäŒç€Ÿ | æèµè£å©è£ 眮åã³æèµè£å©æ¹æ³ |
JP6988579B2 (ja) * | 2018-03-05 | 2022-01-05 | ãããèªåè»æ ªåŒäŒç€Ÿ | å¶åŸ¡è£ 眮åã³å¶åŸ¡æ¹æ³ |
JP7049864B2 (ja) * | 2018-03-05 | 2022-04-07 | Ntnæ ªåŒäŒç€Ÿ | 転èµæ©èœä»ããããŠãããã転èµã·ã¹ãã ãããã³è»¢èµæ©èœä»ããããŠããããåããè»äž¡ |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05229443A (ja) * | 1991-09-04 | 1993-09-07 | Nissan Motor Co Ltd | è»äž¡ã®è£å©æèµè£ 眮 |
JPH05330444A (ja) * | 1991-08-30 | 1993-12-14 | Mazda Motor Corp | è»äž¡ã®ïŒèŒªæèµè£ 眮 |
JPH07223552A (ja) * | 1994-02-15 | 1995-08-22 | Nissan Motor Co Ltd | è»äž¡çšåŸèŒªèµè§å¶åŸ¡è£ 眮 |
JPH07291139A (ja) * | 1994-04-25 | 1995-11-07 | Mazda Motor Corp | è»äž¡ã®åŸèŒªæèµè£ 眮 |
JPH11348798A (ja) * | 1998-06-10 | 1999-12-21 | Hino Motors Ltd | åŸè»žæèµè£ 眮 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2359978A (en) * | 1943-09-02 | 1944-10-10 | John S Edwards | Steering means for vehicles |
US2698668A (en) * | 1952-09-10 | 1955-01-04 | Roy H Mckay | Load equalizing suspension for tandem mounted axles |
US3831961A (en) * | 1973-09-12 | 1974-08-27 | Gen Motors Corp | Steerable tandem axle suspension |
US4373738A (en) * | 1980-04-28 | 1983-02-15 | Lange Dennis M | Steerable auxiliary wheel assembly for vehicles |
US4789038A (en) * | 1987-03-12 | 1988-12-06 | Structural Instrumentation, Inc. | Axle weight distribution controller |
JP2685205B2 (ja) * | 1988-03-14 | 1997-12-03 | ãããæ ªåŒäŒç€Ÿ | è»äž¡ã®åŸèŒªæèµè£ 眮 |
US5163700A (en) * | 1991-01-08 | 1992-11-17 | Terex Corporation | Dual rear axle assembly for large vehicles |
US5607028A (en) * | 1993-11-29 | 1997-03-04 | Braun; Eric E. | All-wheel steering system |
-
1998
- 1998-12-25 JP JP37054498A patent/JP3759681B2/ja not_active Expired - Fee Related
-
2000
- 2000-06-22 WO PCT/JP2000/004111 patent/WO2001098131A1/ja active Application Filing
- 2000-06-22 US US10/049,554 patent/US6763906B1/en not_active Expired - Fee Related
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05330444A (ja) * | 1991-08-30 | 1993-12-14 | Mazda Motor Corp | è»äž¡ã®ïŒèŒªæèµè£ 眮 |
JPH05229443A (ja) * | 1991-09-04 | 1993-09-07 | Nissan Motor Co Ltd | è»äž¡ã®è£å©æèµè£ 眮 |
JPH07223552A (ja) * | 1994-02-15 | 1995-08-22 | Nissan Motor Co Ltd | è»äž¡çšåŸèŒªèµè§å¶åŸ¡è£ 眮 |
JPH07291139A (ja) * | 1994-04-25 | 1995-11-07 | Mazda Motor Corp | è»äž¡ã®åŸèŒªæèµè£ 眮 |
JPH11348798A (ja) * | 1998-06-10 | 1999-12-21 | Hino Motors Ltd | åŸè»žæèµè£ 眮 |
Also Published As
Publication number | Publication date |
---|---|
US6763906B1 (en) | 2004-07-20 |
JP3759681B2 (ja) | 2006-03-29 |
JP2000190865A (ja) | 2000-07-11 |
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