WO2017163406A1 - ボギー車軸装置用バランスシステムおよびボギー車軸装置 - Google Patents
ボギー車軸装置用バランスシステムおよびボギー車軸装置 Download PDFInfo
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- WO2017163406A1 WO2017163406A1 PCT/JP2016/059649 JP2016059649W WO2017163406A1 WO 2017163406 A1 WO2017163406 A1 WO 2017163406A1 JP 2016059649 W JP2016059649 W JP 2016059649W WO 2017163406 A1 WO2017163406 A1 WO 2017163406A1
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- gear
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- driving force
- swing housing
- transmission
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/32—Arrangement or mounting of transmissions in vehicles the ultimate propulsive elements, e.g. ground wheels, being rockable about a horizontal pivot
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
- B60B35/12—Torque-transmitting axles
- B60B35/121—Power-transmission from drive shaft to hub
- B60B35/122—Power-transmission from drive shaft to hub using gearings
- B60B35/125—Power-transmission from drive shaft to hub using gearings of the planetary type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/36—Arrangement or mounting of transmissions in vehicles for driving tandem wheels
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/10—Road Vehicles
- B60Y2200/14—Trucks; Load vehicles, Busses
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/10—Road Vehicles
- B60Y2200/14—Trucks; Load vehicles, Busses
- B60Y2200/142—Heavy duty trucks
- B60Y2200/1422—Multi-axle trucks
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/20—Off-Road Vehicles
- B60Y2200/22—Agricultural vehicles
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/20—Off-Road Vehicles
- B60Y2200/22—Agricultural vehicles
- B60Y2200/222—Harvesters
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/40—Special vehicles
- B60Y2200/41—Construction vehicles, e.g. graders, excavators
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/40—Special vehicles
- B60Y2200/41—Construction vehicles, e.g. graders, excavators
- B60Y2200/411—Bulldozers, Graders
Definitions
- the present invention relates to a bogie axle device that swingably supports two axles arranged in the front-rear direction, a balance system that suppresses swinging that occurs in a swing housing that supports the two axles, and a bogie equipped with the balance system. It relates to a shaft device.
- a harvester that performs tree felling, debranching, and ball cutting, etc., or a forwarder 82 that carries the ball-cut short trunk material on a loading platform 81 with a grapple crane 80 as shown in FIG.
- Self-propelled vehicles such as are used.
- the two axles 83F and 83R arranged in the front-rear direction can be swung with respect to the vehicle.
- a bogie axle device 84 supported as described above.
- the bogie axle device 84 includes a drive unit (not shown) fixed to a vehicle chassis 82a (see FIG. 10) and a pair of left and right axle units 85 swingable with respect to the drive unit. With.
- the drive unit transmits the drive force output from the vehicle engine to the left and right axle units.
- the pair of left and right axle units 85 includes a swing housing 86 that is swingably supported with respect to the drive unit, two axles 83F and 83R that are rotatably supported by the swing housing 86, and a drive that is input from the drive unit.
- a driving force transmission mechanism 87 that transmits force to the two axles 83F and 83R is provided.
- the driving force transmission mechanism 87 includes an input gear 87a to which the driving force of the driving unit is input, and a plurality of gears that transmit the rotation of the input gear 87a to the axles 83F and 83R.
- the ratio of front wheel load: rear wheel load is 50%: 50%.
- the ratio of front wheel load: rear wheel load is, for example, 19.3%: 80.7%.
- the ratio is, for example, 12.3%: 87.7%.
- the swing housing 86 may be reversed when the load balance between the front and rear wheels is largely disrupted by the reaction forces F1 and F2 of the swing torque Ts.
- the load with respect to the axle 83R of a rear wheel becomes large, it is disadvantageous also in terms of strength.
- the reaction forces F1 and F2 of the swinging torque Ts are obtained by the following formulas.
- a conventional bogie axle device is provided with a balance system (see, for example, Patent Document 1 and Patent Document 2).
- the balance system of Patent Document 1 uses two planetary gear mechanisms.
- the carrier output of the first stage planetary gear mechanism is input to the driving force transmission mechanism, and the output from the ring gear of the first stage planetary gear mechanism. Is input to the second planetary gear mechanism.
- the second planetary gear mechanism suppresses swinging of the swing housing by fixing the ring gear to the swing housing and applying swing suppression torque Tb in the direction opposite to the swing torque Ts from the ring gear to the swing housing.
- the driving force input from the driving unit includes a driving force input to the driving force transmission mechanism by the first stage planetary gear mechanism and a reaction force that suppresses swinging of the swing housing.
- the reaction force is amplified by the second stage planetary gear mechanism.
- the balance system of Patent Document 2 uses two planetary gear mechanisms in which each planetary gear group is coaxially held by a common carrier, and swings the swing housing of the ring gear of the first stage planetary gear mechanism.
- the driving force input from the driving unit is amplified, and the amplified driving force is input to the driving force transmission mechanism by the sun gear of the second stage planetary gear mechanism.
- the ring gear of the second planetary gear mechanism is fixed to the swing housing, and the swing restraining torque Tb in the direction opposite to the swing torque Ts is given to the swing housing by the reaction force input from the second planetary gear mechanism. Therefore, swinging of the swing housing is suppressed.
- the driving force input from the driving unit is amplified by the first stage planetary gear mechanism and is input to the driving force transmission mechanism by the second planetary gear mechanism; It is separated into a reaction force that suppresses swinging of the swing housing.
- the effect of suppressing the swing of the swing housing increases as the balance ratio (Tb / Ts), which is the ratio between the swing suppression torque Tb and the swing torque Ts, increases.
- Tb / Ts the balance ratio between the swing suppression torque Tb and the swing torque Ts
- the balance system of Patent Document 1 can obtain a high balance ratio of about 70%, but requires four ring gears and four carriers each.
- the cost increases because there are many parts with complicated structures such as a ring gear that rotates in the planetary gear mechanism of the eye. Further, since the driving force is greatly amplified by the first stage planetary gear mechanism, the strength of the driving force transmission mechanism is disadvantageous.
- the balance system of Patent Document 2 uses only two carriers on the left and right sides, and does not use parts having complicated shapes. Therefore, the balance system of Patent Document 2 is lower in cost and weight. Will also be lighter. However, the balance ratio is as low as about 40%.
- the size of the first stage ring gear is regulated by the slewing bearing, and it is necessary to match the number of teeth of the first and second stage planetary gear mechanisms. You can't make it bigger.
- the driving force input from the drive unit by the first stage planetary gear mechanism is amplified, and the driving force input to the driving force transmission mechanism by the second stage planetary gear mechanism and the reaction force to the swing housing Therefore, the balance ratio cannot be increased by changing only the reduction ratio on the reaction force side.
- the present invention aims to provide a bogie axle device and a balance system that can obtain a high balance ratio at a low cost.
- a first aspect of the present invention is directed to a drive unit fixed to a vehicle chassis, a swing housing that is swingably supported by the drive unit, and a swing housing that is rotatably supported by the swing housing.
- a bogie axle device including a pair of front and rear axles and a driving force transmission mechanism that transmits driving force input from the drive unit to the pair of front and rear axles, and suppresses swinging that occurs in the swing housing when the vehicle travels System.
- This balance system includes a reaction force separation mechanism and a planetary gear mechanism.
- the reaction force separation mechanism includes an input gear to which driving force is input from the driving unit, an output gear that outputs driving force to the driving force transmission mechanism, a first transmission gear that meshes with the input gear, and a first transmission gear. And a second transmission gear that meshes with the output gear, and a first carrier that holds these gears and is rotatable on the outer periphery of the input gear and the output gear.
- the planetary gear mechanism includes a sun gear that rotates integrally with a first carrier, a planetary gear group that is supported by a second carrier fixed to a drive unit and meshes with the sun gear, and a planetary gear that is fixed to a swing housing. A ring gear meshing with the group.
- the reaction force is separated from the driving force inputted by the reaction force separation mechanism, and the reaction force is shifted and inputted to the planetary gear mechanism.
- the input reaction force is amplified and input to the swing housing.
- the first transmission gear and the second transmission gear are a plurality of pieces arranged on the outer circumferences of the input gear and the output gear, respectively. It consists of a gear group.
- the input gear and the output gear are arranged to rotate in different planes, and the first transmission gear and One of the second transmission gears has a wide tooth width so as to be meshed with the rotation surfaces of the input gear and the output gear.
- a drive unit fixed to a vehicle chassis, a swing housing that is swingably supported by the drive unit, and a pair of front and rear axles that are rotatably supported by the swing housing;
- a bogie that includes a pair of axle units including a driving force transmission mechanism that transmits a driving force input from the driving unit to a pair of front and rear axles, and a balance system that suppresses swinging that occurs in the swing housing when the vehicle is traveling It is a shaft device.
- the balance system includes a reaction force separation mechanism and a planetary gear mechanism.
- the reaction force separation mechanism includes an input gear to which driving force is input from the driving unit, an output gear that outputs driving force to the driving force transmission mechanism, a first transmission gear that meshes with the input gear, and a first transmission gear. And a second transmission gear that meshes with the output gear, and a first carrier that holds these gears and is rotatable on the outer periphery of the input gear and the output gear.
- the planetary gear mechanism includes a sun gear that rotates integrally with a first carrier, a planetary gear group that is supported by a second carrier fixed to a drive unit and meshes with the sun gear, and a planetary gear that is fixed to a swing housing. A ring gear meshing with the group.
- the cost can be reduced as compared with the balance system of Patent Documents 1 and 2.
- the reaction force separation mechanism the reaction force is separated from the driving force of the drive unit without using a ring gear, and then the reaction force is amplified by the planetary gear mechanism.
- swinging of the swing housing can be appropriately suppressed in various types of bogie axle devices.
- the first transmission gear and the second transmission gear are composed of a plurality of gear groups, the input gear, the first transmission gear, the first transmission gear, and the second transmission gear are arranged. Shifting between the transmission gear, the second transmission gear, and the output gear can be performed stably.
- the reaction force separation is performed.
- the mechanism can be miniaturized.
- FIG. 4 is a cross-sectional view taken along the line AA in FIG. 3 showing the configuration of the reaction force separating mechanism.
- FIG. 4 is a cross-sectional view taken along the line BB in FIG. 3 showing the configuration of the reaction force separating mechanism.
- FIG. 4 is a cross-sectional view taken along the line CC of FIG. 3 showing the configuration of the reaction force separating mechanism.
- FIG. 6 is an explanatory diagram showing a reaction force separation mechanism of a second embodiment. It is a side view of a forwarder using a bogie axle device. It is a side view which shows the structure of the conventional bogie axle apparatus.
- the bogie axle device 1 includes a drive unit 2 fixed to a chassis of a vehicle such as a harvester or a forwarder, a pair of left and right axle units 3L and 3R swingable with respect to the drive unit 2, and a drive unit 2 and an axle unit 3L. 3R, and a pair of left and right balance systems 4L, 4R provided between them.
- the drive unit 2 includes an input unit 21 into which a driving force output from a vehicle engine is input by a drive shaft (not shown), and a substantially cylindrical unit housing 22 provided with the input unit 21 on the front side of the vehicle.
- the brake housings 23L and 23R having substantially cylindrical shapes attached to the left and right ends of the unit housing 22 are provided.
- a differential mechanism for transmitting the driving force input to the input unit 21 to the left and right axle units 3L and 3R is accommodated.
- a brake mechanism for stopping the rotation of the axle is incorporated in the brake housings 23L and 23R.
- the unit housing 22 and the brake housings 23L, 23R are connected by a plurality of bolts that are inserted into mounting holes provided in the brake housings 23L, 23R and screwed into the unit housing 22.
- the axle unit 3L is provided in a swing housing 31L supported so as to be swingable with respect to the drive unit 2, two axles 32LF and 32LR rotatably supported by the swing housing 31L, and the swing housing 31L. And a driving force transmission mechanism 33L that transmits the driving force input from the driving unit 2 to the two axles 32LF and 32LR.
- the driving force transmission mechanism 33L includes an input gear 331L to which the driving force of the driving unit 2 is input, and a plurality of gears 332L and 333L that transmit the rotation of the input gear 331L to the axles 32LF and 32LR. Tires (not shown) are attached to the axles 32LF and 32LR, respectively. Since the axle unit 3R has the same configuration as the axle unit 3L, detailed description thereof is omitted.
- the balance unit 4L includes a reaction force separating mechanism 41L, a planetary gear, as shown in FIGS. 3 to 5 and FIGS. 6 to 8 showing the AA, BB, and CC sections of FIG. A mechanism 42L and a turning bearing 43L are provided.
- the reaction force separation mechanism 41L separates the driving force input from the driving unit 2 into a driving force transmitted to the driving force transmission mechanism 33L and a reaction force transmitted to the planetary gear mechanism 42L.
- the planetary gear mechanism 42L includes a sun gear 421L that rotates integrally with the first carrier of the reaction force separation mechanism 41L, a second carrier 422L that is fixed to the brake housing 23L of the drive unit 2, and a second carrier 422L.
- a planetary gear group 423L that is supported and meshes with the sun gear 421L, an annular holding plate 424L that retains the planetary gear group 423L on the second carrier 422L, and a mesh with the planetary gear group 423L that is fixed to the swing housing 31L.
- Ring gear 425L is provided to the sun gear 421L, a second carrier 422L that is fixed to the brake housing 23L of the drive unit 2, and a second carrier 422L.
- the slewing bearing 43L is a rolling ball bearing that swingably supports the swing housing 31L, and uses a common bolt and the inner ring 431L fixed to the brake housing 23L together with the second carrier 422L using a common bolt.
- the ring gear 425L and the outer ring 432L fixed to the swing housing 31L are provided.
- the reaction force separation mechanism 41L includes an input gear 411L, a first transmission gear group 412L, a second transmission gear group 413L, an output gear 414L, an inner carrier 415L and an outer carrier 416L constituting the first carrier, Is provided.
- the input gear 411L is integrally provided with an input shaft 411La to which a driving force is input from the drive unit 2.
- the input gear 411L is rotatably accommodated in the first carrier, and the input shaft 411La is inserted into the drive unit 2 through an opening 415La provided in the inner carrier 415L.
- the first transmission gear group 412L is rotatably held by the first carrier and meshes with the input gear 411L.
- the second transmission gear group 413L is rotatably held by the first carrier, and the first transmission gear group 413L has a wider tooth width than the first transmission gear group 412L.
- the gear group 412L meshes with the output gear 414L.
- the output gear 414L is integrally provided with an output shaft 414La that outputs a driving force to the driving force transmission mechanism 33L.
- the output gear 414L is rotatably accommodated in the first carrier, and the output shaft 414La is inserted into the swing housing 31L through an opening 416La provided in the outer carrier 416L.
- An input gear 331 of the driving force transmission mechanism 33L is attached to the tip of the output shaft 414La.
- the inner carrier 415L and the outer carrier 416L are rotatably supported by the second carrier 422L and the brake housing 23L via the annular sleeves 44La and 44Lb shown in FIG. 4, and the input gear 411L and the output gear 414L Rotate around In the opening 416La of the outer carrier 416L, a tooth row is provided along the axial direction, and a cylindrical coupling 45L in which the tooth row is provided along the axial direction on the outer peripheral surface is inserted and meshed. .
- An opening through which the output shaft 414La is inserted is provided in the coupling 45L.
- the sun gear 421L of the planetary gear mechanism 42L meshes with the tip of the coupling 45L. Thereby, the sun gear 421L rotates integrally with the first carrier. Since the balance system 4R has the same configuration as the balance system 4L, detailed description thereof is omitted.
- the operation of the above embodiment will be described.
- the input gear 411L rotates.
- the rotation of the input gear 411L is transmitted to the output gear 414L by the first transmission gear group 412L and the second transmission gear group 413L.
- the rotation of the output shaft 414La provided integrally with the output gear 414L is transmitted to the axles 32LF and 32LR via the input gear 331L and the driving force transmission mechanism 33L.
- the tires attached to the axles 32LF and 32LR rotate, so that the vehicle provided with the bogie axle device 1 starts running.
- the planetary gear mechanism 42L amplifies the reaction force input to the sun gear 421L by the planetary gear group 423L and the ring gear 425L and transmits the amplified reaction force to the swing housing 31L.
- fluctuation suppression torque Tb which suppresses rocking
- fluctuation of the swing housing 31L is suppressed.
- the balance ratio (Tb / Ts), which is the ratio of the swing suppression torque Tb and the swing torque Ts, is approximately 90%. Thus, it is possible to obtain a rocking suppression effect higher than that of the balance system 2.
- the cost is lower than that of the conventional balance system. Can be reduced.
- the reaction force is separated from the drive force of the drive unit 2 by the reaction force separation mechanism 41L and then the reaction force is amplified by the planetary gear mechanism 42L, the change of the reaction force speed ratio becomes easy.
- the swing of the swing housing 31L can be appropriately suppressed in various types of bogie axle devices.
- first transmission gear and the second transmission gear are composed of a plurality of gear groups 412L, 413L, the input gear 411L, the first transmission gear group 412L, the first transmission gear group 412L, and the second transmission gear group. Shifting between the gear group 413L, the second transmission gear group 413L, and the output gear 414L can be performed stably. Further, since the input gear 411L and the output gear 414L are connected by widening the tooth width of the second transmission gear group 413L, the reaction force separation mechanism 41L can be reduced in size.
- FIG. 9 shows a schematic side view of gears constituting the reaction force separation mechanism and a plan view of gears on the input side and the output side, and a structure in which the driving force is decelerated by the reaction force separation mechanism (A ), An amplifying configuration (B), and a non-shifting configuration (C).
- the first transmission gear 52 is engaged with the input gear 51 having a relatively small number of teeth on the same surface, and the first transmission gear 52 is engaged with the first transmission gear 52.
- the second transmission gear 53 is engaged, and the output gear 54 having more teeth than the input gear 51 is engaged with the second transmission gear 53.
- the diameter of the input gear 51 is relatively small, and a space for arranging the second transmission gear 53 on the same surface is obtained. Therefore, as in the first embodiment, the first stage on the input side is provided. Seven gears can be arranged, and four gears can be arranged on the second stage on the output side.
- the first transmission gear 62 is engaged with the input gear 61 having a relatively large fraction
- the second transmission gear 62 is engaged with the second transmission gear 62.
- the transmission gear 63 is meshed, and the output gear 64 having fewer teeth than the input gear 61 is meshed with the second transmission gear 63.
- the diameter of the input gear 61 becomes relatively large, and a space for disposing the second transmission gear 63 on the same surface cannot be obtained. Therefore, four gears are disposed in the first stage and become the output side. It is necessary to arrange seven gears in the second stage. That is, when the driving force is increased, it is necessary to reverse the gear arrangement on the input side and the output side as compared with the case where the driving force is reduced.
- the input gear 71 is engaged with the first transmission gear 72 and the first transmission gear 72 is engaged with the first transmission gear 72.
- the second transmission gear 73 is engaged, and the second transmission gear 73 is engaged with the output gear 74 having the same number of teeth as the input gear 71.
- the gear arrangement between the input side and the output side is divided into three stages, the first transmission gear 72 is divided into two parts on the input side and the output side, and the output gear 74 is arranged therebetween. By doing so, interference between the first transmission gear 72 and the output gear 74 can be avoided.
- the bogie device and the balance system of the present invention can be used for self-propelled vehicles that require high traveling performance, such as agricultural tractors, harvesters, combine harvesters, etc., as well as scrapers for construction machinery. .
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Abstract
Description
To=Ti×i
F=To/R
F’=F
TS=F’×L
To:タイヤ回転トルク
F:タイヤ接地面の接線力
F’:スウィングハウジングが受ける反力
Ts:揺動トルク
Ti:駆動力伝達機構への入力トルク
i:駆動力伝達機構の減速比
R:タイヤ半径
L:揺動中心から地面までの高さ
F1=F2=Ts/L2
L2:車軸間の距離
図1~図3は、本実施の形態のボギー車軸装置1の外観斜視図、一部分解斜視図および要部断面図である。ボギー車軸装置1は、ハーベスタやフォワーダなどの車両のシャーシに固定される駆動ユニット2と、駆動ユニット2に対して揺動自在な左右一対の車軸ユニット3L、3Rと、駆動ユニット2と車軸ユニット3L、3Rとの間にそれぞれ設けられた左右一対のバランスシステム4L、4Rとを備える。
次に、本発明の第2の実施の形態について説明する。なお、第1の実施の形態と同部品については、同符号を用いて詳しい説明は省略する。実施の形態1では、反力分離機構41Lにより駆動ユニット2から入力された駆動力を減速する例について説明したが、本発明の反力分離機構は、駆動力を増速すること、あるいは変速せずにそのまま出力することもできる。
2 駆動ユニット
3L、3R 車軸ユニット
31L スウィングハウジング
32LF、32LR 車軸
33L 駆動力伝達機構
4L、4R バランスシステム
41L 反力分離機構
411L 入力ギヤ
412L 第1の変速ギヤ群
413L 第2の変速ギヤ群
414L 出力ギヤ
415l 内側キャリア(第1のキャリア)
416L 外側キャリア(第1のキャリア)
42L 遊星歯車機構
421L 太陽ギヤ
422L 第2のキャリア
425L リングギヤ
Claims (4)
- 車両のシャーシに固定された駆動ユニットと、前記駆動ユニットに揺動自在に支持されたスウィングハウジングと、前記スウィングハウジングに回転自在に支持された前後一対の車軸と、前記駆動ユニットから入力された駆動力を前記前後一対の車軸に伝達する駆動力伝達機構とを備えるボギー車軸装置に用いられ、前記車両の走行時に前記スウィングハウジングに生じる揺動を抑えるバランスシステムであって、
前記駆動ユニットから駆動力が入力される入力ギヤと、前記駆動力伝達機構に駆動力を出力する出力ギヤと、前記入力ギヤに噛合する第1の変速ギヤと、前記第1の変速ギヤおよび前記出力ギヤに噛合する第2の変速ギヤと、これらのギヤを保持し、前記入力ギヤおよび前記出力ギヤの外周で回転自在な第1のキャリアと、を備える反力分離機構と、
前記第1のキャリアと一体に回転する太陽ギヤと、前記駆動ユニットに固定された第2のキャリアに支持されて前記太陽ギヤと噛合する遊星ギヤ群と、前記スウィングハウジングに固定されて前記遊星ギヤ群と噛合するリングギヤとを備え、前記スウィングハウジングに揺動を抑えるための反力を伝達する遊星歯車機構と、
を備えることを特徴とするボギー車軸装置用バランスシステム。 - 前記第1の変速ギヤおよび前記第2の変速ギヤは、前記入力ギヤおよび前記出力ギヤの外周にそれぞれ配置された複数のギヤ群からなる、
ことを特徴とする請求項1に記載のボギー車軸装置用バランスシステム。 - 前記入力ギヤと前記出力ギヤは、異なる面内で回転するように配置されており、前記第1の変速ギヤと前記第2の変速ギヤのいずれか一方は、前記入力ギヤと前記出力ギヤの回転面で噛合可能なように歯幅が広くなっている、
ことを特徴とする請求項1または2に記載のボギー車軸装置用バランスシステム。 - 車両のシャーシに固定された駆動ユニットと、前記駆動ユニットに揺動自在に支持されたスウィングハウジングと、前記スウィングハウジングに回転自在に支持された前後一対の車軸と、前記駆動ユニットから入力された駆動力を前記前後一対の車軸に伝達する駆動力伝達機構とを備える左右一対の車軸ユニットと、前記車両の走行時に前記スウィングハウジングに生じる揺動を抑えるバランスシステムと、を備えるボギー車軸装置であり、
前記バランスシステムは、
前記駆動ユニットから駆動力が入力される入力ギヤと、前記駆動力伝達機構に駆動力を出力する出力ギヤと、前記入力ギヤに噛合する第1の変速ギヤと、前記第1の変速ギヤおよび前記出力ギヤに噛合する第2の変速ギヤと、これらのギヤを保持し、前記入力ギヤおよび前記出力ギヤの外周で回転自在な第1のキャリアと、を備える反力分離機構と、
前記第1のキャリアと一体に回転する太陽ギヤと、前記駆動ユニットに固定された第2のキャリアに支持されて前記太陽ギヤと噛合する遊星ギヤ群と、前記スウィングハウジングに固定されて前記遊星ギヤ群と噛合するリングギヤとを備え、前記スウィングハウジングに揺動を抑えるための反力を伝達する遊星歯車機構と、
を備えることを特徴とするボギー車軸装置。
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EP16895437.8A EP3434505B1 (en) | 2016-03-25 | 2016-03-25 | Bogie axle device balance system and bogie axle device |
PCT/JP2016/059649 WO2017163406A1 (ja) | 2016-03-25 | 2016-03-25 | ボギー車軸装置用バランスシステムおよびボギー車軸装置 |
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Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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EP0909671A2 (de) | 1997-10-15 | 1999-04-21 | Neunkirchener Maschinen- und Achsenfabrik GmbH & Co. KG | Antriebsanordnung für eine Tandemachse |
US20060102407A1 (en) * | 2004-10-29 | 2006-05-18 | Raynald Berthiaume | Log skidder |
US20110245012A1 (en) * | 2008-12-18 | 2011-10-06 | Schaeffler Technologies Gmbh & Co. Kg | Spur gear differential |
EP2657059A1 (de) | 2012-04-24 | 2013-10-30 | NAF Neunkirchener Achsenfabrik AG | Antriebsvorrichtung für Tandemachsen |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
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DE2522542C3 (de) * | 1975-05-21 | 1979-11-15 | Valmet Oy, Helsinki | Antriebsanordnung eines Kraftfahrzeuges |
DE4120801A1 (de) * | 1991-06-24 | 1993-01-21 | Neunkirchner Masch Achsen | Antriebsvorrichtung fuer tandemachsen |
EP1902891B1 (de) * | 2006-09-22 | 2009-01-07 | NAF Neunkirchener Achsenfabrik AG | Antriebsvorrichtung für Tandemachsen und Verfahren zum Antrieb von Tandemachsen |
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- 2016-03-25 EP EP16895437.8A patent/EP3434505B1/en active Active
- 2016-03-25 JP JP2018506728A patent/JP6599547B2/ja active Active
- 2016-03-25 WO PCT/JP2016/059649 patent/WO2017163406A1/ja active Application Filing
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0909671A2 (de) | 1997-10-15 | 1999-04-21 | Neunkirchener Maschinen- und Achsenfabrik GmbH & Co. KG | Antriebsanordnung für eine Tandemachse |
US6053837A (en) * | 1997-10-15 | 2000-04-25 | Neunkirchener Maschinen - Und Achsenfabrik Gmbh & Co. Kg | Drive unit for a tandem axle |
US20060102407A1 (en) * | 2004-10-29 | 2006-05-18 | Raynald Berthiaume | Log skidder |
US20110245012A1 (en) * | 2008-12-18 | 2011-10-06 | Schaeffler Technologies Gmbh & Co. Kg | Spur gear differential |
EP2657059A1 (de) | 2012-04-24 | 2013-10-30 | NAF Neunkirchener Achsenfabrik AG | Antriebsvorrichtung für Tandemachsen |
Non-Patent Citations (1)
Title |
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EP3434505A4 (en) | 2020-02-26 |
EP3434505B1 (en) | 2022-05-11 |
EP3434505A1 (en) | 2019-01-30 |
JPWO2017163406A1 (ja) | 2019-01-24 |
JP6599547B2 (ja) | 2019-10-30 |
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