JPS63258222A - Regular four-wheel driving system - Google Patents
Regular four-wheel driving systemInfo
- Publication number
- JPS63258222A JPS63258222A JP8989987A JP8989987A JPS63258222A JP S63258222 A JPS63258222 A JP S63258222A JP 8989987 A JP8989987 A JP 8989987A JP 8989987 A JP8989987 A JP 8989987A JP S63258222 A JPS63258222 A JP S63258222A
- Authority
- JP
- Japan
- Prior art keywords
- worm
- gear
- planetary carrier
- transmission gear
- wheel drive
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000005540 biological transmission Effects 0.000 claims abstract description 12
- 230000009977 dual effect Effects 0.000 abstract 2
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 239000000969 carrier Substances 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Landscapes
- Arrangement And Driving Of Transmission Devices (AREA)
- Retarders (AREA)
Abstract
Description
【発明の詳細な説明】
(イ) 産業上の利用分野
この発明は、常時四輪駆動装置の改良に関する(口)
従来の技術
4個のウオーム及ウオーム歯車を使用する2重差動装置
のプラネタリキャリヤを中心の主軸により回転するには
、ウオームの連動平歯車の径が大きくなりプラネタリキ
ャリヤ全体も大型化する問題点があった。[Detailed description of the invention] (a) Industrial application field This invention relates to improvement of a constant four-wheel drive device.
Conventional technology In order to rotate the planetary carrier of a double differential device using four worms and worm gears by the central main shaft, the diameter of the interlocking spur gear of the worm becomes large, and the overall planetary carrier also becomes large. was there.
(ハ) 発明が解決しようとする問題点この発明は、ウ
オーム及ウオーム歯車を使用する2重差動装置に於て、
其伝動平歯車を2組増加しただけで、異径を同一にして
、全体を小型軽量且簡単な常時四輪駆動装置を得る事を
目的としている。(c) Problems to be Solved by the Invention This invention solves the following problems in a double differential device using a worm and a worm gear.
The purpose is to obtain a constant four-wheel drive device that is small, lightweight, and simple as a whole by adding only two sets of transmission spur gears and making the different diameters the same.
(ニ) 問題点を解決するだめの手段
以下、この発明を図面について説明する。第1図は、こ
の発明の4ウオーム逆転型で第1実施例の2重差動装置
の構造を示す平断面図であシ、第2図は、其パワートレ
インをスケルトンで示す平面概略図である。2重差動装
置1のプラネタリキャリヤ2に4個の前ウオーム3、前
内ウォーム4、後内ウォーム5及後ウオーム6の各ウオ
ームが第3図示のように各3個設けられている。第4図
示のように前ウオーム3と同体の連動ギヤ7は前内ウォ
ーム4軸上のアイドラーギヤ8、プラネタリキャリヤ2
上の中間ギヤ9後内ウオーム5と同体の連動ギヤ10を
介して、連動する構成であり、同様に前内ウォーム4と
同体の連動ギヤ11はプラネタリキャリヤ2上の中間ギ
ヤ12及後内ウオーム5軸上のアイドラーギヤ13を介
して、後ウオーム6と同体の連動ギヤ14を介し、後ウ
オーム6を連動する構造である。これらは、車輛の転回
時に、前ウオーム3と後内ウォーム5、及前内ウォーム
4と後ウオーム6との間で2組の差動回転を同一主軸1
70回転によシプラネタリキャリャ2を介して行う事は
、特願昭60−279117号の明細書に記載された発
明の作用、効果と同一のものである。(d) Means for solving the problems The present invention will be explained below with reference to the drawings. FIG. 1 is a plan sectional view showing the structure of a four-worm reversing type double differential of the first embodiment of the present invention, and FIG. 2 is a plan schematic view showing the power train in a skeleton form. be. The planetary carrier 2 of the double differential gear 1 is provided with three each of four worms: a front worm 3, a front inner worm 4, a rear inner worm 5, and a rear worm 6, as shown in the third figure. As shown in the fourth diagram, the interlocking gear 7 that is integral with the front worm 3 is an idler gear 8 on the front inner worm 4 axis, and a planetary carrier 2.
The upper intermediate gear 9 is configured to interlock with the rear inner worm 5 through an interlocking gear 10, and similarly, the interlocking gear 11, which is also the same as the front inner worm 4, is connected to the intermediate gear 12 on the planetary carrier 2 and the rear inner worm. The structure is such that the rear worm 6 is interlocked via an idler gear 13 on five axes and an interlocking gear 14 that is integral with the rear worm 6. When the vehicle turns, two sets of differential rotation between the front worm 3 and the rear inner worm 5, and between the front inner worm 4 and the rear worm 6 are transmitted to the same main shaft.
The operation and effect of the 70 revolutions via the planetary carrier 2 are the same as those of the invention described in the specification of Japanese Patent Application No. 60-279117.
(ホ) 作用
エンジン15の出カバ、トランスミッション16、主軸
17を介して、プラネタリキャリヤディスク18を通し
て、プラネタリキャリヤ2を回転し、前ウオーム歯車1
9は後内ウォーム歯車2oに連動し、中軸21、ユニバ
ーサルジヨイント22、内プロペラシャフト23、後ピ
ニオン24、右ベベルギヤ25、リツジドアクスル26
内の右軸27、右ドライブギヤ28及右減速歯車29を
介して、右後車軸30を回転する。同時に、前内ウォー
ム歯車31の回転は後ウオーム歯車32に連動し、中空
軸33、公知のラバージヨイント34、外プロペラシャ
フト35、前ビニオン36、左ベベルギヤ37、左軸3
8、左ドライブギヤ39及左減速歯車40を介して左後
車軸41を回転する。第5図示のように、左右軸38.
27は平行であるが間隔があるため、左右後車輪42.
43に隣接して設けられた左右ドライブギヤ39.28
は左右減速歯車(ヘリカルギヤ)40.29に各々ずれ
てかみ合っている。前ウオーム歯車19の回転は、主軸
17上の中空軸44、左トランスファードライブギヤ4
5、左トランスファードリブンギヤ46、ユニバーサル
ジヨイント(叉はボールジヨイント)47、左プロペラ
クヤフト48、左ビニオン49、左ハイポイドギヤ50
及ボールジヨイント51を介して、左前車軸52を駆動
する。前内ウォーム歯車53の回転は、主軸17と中空
軸44の中間の環状軸54、右トランスファードライブ
ギヤ55、右トランスファードリブンギヤ56、ユニバ
ーサルジヨイント47、右プロペラシャフト57、右ピ
ニオン58、右ハイポイドギヤ59及ボールジヨイント
51を介して、右前車軸60を駆動する。左右プロペラ
シャフト48.57は内外プロペラシャツ)23.35
とともにY字型のパワートレーンを形成して、左右ギヤ
ボックス61.62を左右サスペンションアーム63.
64上に設けられる為鬼パワートレーン全体が簡略化さ
れる利点がある。各ウオーム3.4.5.6は共に4個
の連動ギヤ7.8.9.10を両側に連動させて駆動す
るためギヤのタイムラグは同一となる利点があシ、これ
らはケーシング65内に収容されている。後ギヤボック
ス80は小型化され左右減速歯車40.29より高い位
置にリツジドアクスル26を配置する為、最低地上高を
著しく高くとれる利点がある。この実施例は昭61−2
20973号の明細書に記載されたパワートレインに類
はし、主軸17からプラネタリキャリヤ2叉はプラネタ
リキャリヤ2から主軸17へ出力の出し入れが必要な2
重差動装置1が小型、軽量化される。(E) Operation The planetary carrier 2 is rotated through the output cover of the engine 15, the transmission 16, and the main shaft 17 through the planetary carrier disk 18, and the front worm gear 1 is rotated.
9 is interlocked with the rear inner worm gear 2o, and includes a center shaft 21, a universal joint 22, an inner propeller shaft 23, a rear pinion 24, a right bevel gear 25, and a rigid axle 26.
The right rear axle 30 is rotated through the inner right shaft 27, right drive gear 28, and right reduction gear 29. At the same time, the rotation of the front inner worm gear 31 is linked to the rear worm gear 32, which includes a hollow shaft 33, a known rubber joint 34, an outer propeller shaft 35, a front pinion 36, a left bevel gear 37, and a left shaft 3.
8. Rotate the left rear axle 41 via the left drive gear 39 and left reduction gear 40. As shown in Figure 5, the left and right axis 38.
27 are parallel, but there is a gap between them, so the left and right rear wheels 42.
Left and right drive gear 39.28 provided adjacent to 43
are meshed with the left and right reduction gears (helical gears) 40.29 with respective deviations. The rotation of the front worm gear 19 is caused by the hollow shaft 44 on the main shaft 17 and the left transfer drive gear 4.
5. Left transfer driven gear 46, universal joint (or ball joint) 47, left propeller shaft 48, left binion 49, left hypoid gear 50
The left front axle 52 is driven via the ball joint 51. The front inner worm gear 53 is rotated by an annular shaft 54 located between the main shaft 17 and the hollow shaft 44, a right transfer drive gear 55, a right transfer driven gear 56, a universal joint 47, a right propeller shaft 57, a right pinion 58, and a right hypoid gear 59. The right front axle 60 is driven via the ball joint 51. Left and right propeller shafts 48.57 are inner and outer propeller shirts) 23.35
Together, they form a Y-shaped power train, with left and right gearboxes 61, 62 connected to left and right suspension arms 63.
64, it has the advantage of simplifying the entire power train. Since each worm 3.4.5.6 drives four interlocking gears 7.8.9.10 on both sides, the time lag of the gears is the same, which is an advantage. It is accommodated. Since the rear gearbox 80 is downsized and the rigid axle 26 is disposed at a higher position than the left and right reduction gears 40.29, it has the advantage of significantly increasing the minimum ground clearance. This example is 1986-2.
Similar to the power train described in the specification of No. 20973, there are two systems in which output must be taken in and out from the main shaft 17 to the planetary carrier 2 or from the planetary carrier 2 to the main shaft 17.
The heavy differential device 1 is made smaller and lighter.
(へ) 実施例
第1図示の第1実施例の4ウオーム逆転型はエンジン縦
置車で高床式オフロード用の車輛に適するが、第6図示
の第2実施例は一般道路用の車輛に適した一例であシ、
左右ハイポイドギヤ50.59はボールジヨイント66
、左右プロペラシャフト67.68を介して、左右前車
軸52.60を回転し、後ギヤボックス69内の前ビニ
オン70が左ハイポイドギヤ71、ユニバーサルジヨイ
ント72及左プロペラシヤフト73を介して、左後車軸
41を駆動し、後ピニオン74が右ハイポイドギヤ75
、ユニバーサルジヨイント72及左プロペラシヤフト7
6を介して、右後車軸30を駆動°する。内外プロペラ
シャフト23.35は車の中心線に対して4° (図示
例)傾斜している。第7図は2ウオーム正転型でプラネ
タリキャリヤ82を左右(エンジン横置車用)叉は前後
(エンジン縦置車用)に分離して2重差動装置を形成す
る場合の実施例であり、前ウオーム83と同体の連動ギ
ヤ84は両端に設けられ、2個の中間ギヤ85の間にプ
ラネタリキャリヤディスク86を設けてあシ、前内ウォ
ーム87と同体の連動ギヤ88によυ前つオーム83と
前内ウォーム87(叉は同様に後内ウォームと後ウオー
ム)との間で差動回転するものであり、この場合前ウオ
ーム83と前内ウォーム87は同方向に連動回転する為
、其ねじれは逆方向となる。前ウオーム歯車及前内ウォ
ーム歯車は第3図示の第1実施例と同じ形状であるが、
其ねじれは前ウオーム83と前内ウォーム87に合わせ
て互に逆になる。第8図示の4ウオーム正転型用のプラ
ネタリキャリヤ89は、第4図示の第1実施例のプラネ
タリキャリヤ2と同様前ウオーム90、前内ウォーム9
1、後内ウォーム92、後ウオーム93の4個のウオー
ムを取付けだものであるが、前ウオーム90と同体の連
動ギヤ94が前内ウォーム91の軸上のアイドラーギヤ
95、プラネタリキャリヤディスク96上の中間ギヤ9
7、後内ウォーム92の軸上のアイドラーギヤ99、後
ウオーム93と同体の連動ギヤ100を介して、前ウオ
ーム90の回転を後ウオーム93に連動回転する。同時
に前内ウォーム91と同体の連動ギヤ101が中間ギヤ
102、後内ウォーム92と同体の連動ギヤ103を介
して、前内ウォーム91の回転を後内ウォーム92に連
動回転する。この場合前ウオーム90と前内ウォーム9
1のねじれに対して後内ウォーム92と後ウオーム93
のねじれは互に逆になっている。この実施例のプラネタ
リキャリヤ89を使用した2重差動装置(図示せず)を
第1及第2実施例に応用する場合前ウオーム歯車19が
右トランスファードリブンギヤ56を連動し、前内ウォ
ーム歯車31が左トランスファードリブンギヤ46を連
動すれ・ばよく、各実施例の用途に応じてこれらのプラ
ネタリキャリヤ2.82.89を使用した2重差動装置
1を多種多様に使い分ける事が出来る。(v) Embodiment The 4-worm reversible type of the first embodiment shown in the first diagram is suitable for a vehicle with a longitudinally installed engine and a high-floor off-road vehicle, but the second embodiment shown in the sixth diagram is suitable for a vehicle for general roads. A suitable example is
Left and right hypoid gears 50.59 are ball joints 66
, the left and right front axles 52,60 are rotated through the left and right propeller shafts 67,68, and the front binion 70 in the rear gear box 69 is rotated through the left hypoid gear 71, the universal joint 72, and the left propeller shaft 73, and the left rear The rear pinion 74 drives the axle 41 and the right hypoid gear 75
, universal joint 72 and left propeller shaft 7
6, the right rear axle 30 is driven. The inner and outer propeller shafts 23.35 are inclined at 4° (example shown) with respect to the center line of the car. FIG. 7 shows an embodiment in which a two-worm forward rotation type planetary carrier 82 is separated into left and right (for vehicles with horizontal engine) or front and rear (for vehicles with vertical engine) to form a double differential. An interlocking gear 84, which is integral with the front worm 83, is provided at both ends, and a planetary carrier disk 86 is provided between two intermediate gears 85. It rotates differentially between the ohm 83 and the front inner worm 87 (or similarly, the rear inner worm and the rear worm), and in this case, the front worm 83 and the front inner worm 87 rotate in conjunction with each other in the same direction. The twist is in the opposite direction. The front worm gear and the front inner worm gear have the same shape as the first embodiment shown in the third figure, but
The torsions thereof are reversed in accordance with the front worm 83 and the front inner worm 87. The planetary carrier 89 for the 4-worm normal rotation type shown in FIG. 8 has a front worm 90, a front inner worm 9,
1. The four worms, the rear inner worm 92 and the rear worm 93, are installed, and the interlocking gear 94, which is the same as the front worm 90, is connected to the idler gear 95 on the shaft of the front inner worm 91, and on the planetary carrier disk 96. intermediate gear 9
7. The front worm 90 is rotated in conjunction with the rear worm 93 via an idler gear 99 on the shaft of the rear inner worm 92 and an interlocking gear 100 that is integral with the rear worm 93. At the same time, an interlocking gear 101 that is integral with the front inner worm 91 rotates the front inner worm 91 in conjunction with the rear inner worm 92 via an intermediate gear 102 and an interlocking gear 103 that is integral with the rear inner worm 92. In this case, the front worm 90 and the front inner worm 9
The rear inner worm 92 and the rear worm 93 for the twist of 1
The twists are opposite to each other. When the double differential device (not shown) using the planetary carrier 89 of this embodiment is applied to the first and second embodiments, the front worm gear 19 interlocks the right transfer driven gear 56, and the front inner worm gear 31 It is only necessary that the left transfer driven gear 46 be interlocked with the left transfer driven gear 46, and the double differential device 1 using these planetary carriers 2, 82, 89 can be used in a wide variety of ways depending on the application of each embodiment.
(ト) 発明の効果
この発明は、以上のように其2重差動装置1のウオーム
の連動ギヤの一部にプラネタリキャリヤ2上の中間ギヤ
9.12を用いて、主軸17よシプラネタリキャリャデ
ィスク18を介して、プラネタリキャリヤ2を回転する
事により、各連動ギヤは公知のトーセンデフのギヤと同
一の径でよく、プラネタリキャリヤ2の外径も増大せず
、全体を小型1量にし其コストを低減し得る効果がある
。更に第7.8図示のプラネタリキャリヤ82.89を
使用した2重差動装置を適用する場合も同様に其外径は
増大せず、異名用範囲を拡充する。(G) Effects of the Invention As described above, the present invention uses the intermediate gears 9 and 12 on the planetary carrier 2 as part of the interlocking gear of the worm of the double differential device 1, so that the planetary carrier is connected to the main shaft 17. By rotating the planetary carrier 2 through the rear disk 18, each interlocking gear can have the same diameter as the gear of a known tosen differential, the outer diameter of the planetary carrier 2 does not increase, and the entire unit can be made into a small unit. This has the effect of reducing costs. Furthermore, when a double differential device using a planetary carrier 82.89 shown in Fig. 7.8 is applied, the outer diameter does not increase, and the range of different names is expanded.
第1図は、この発明の4ウオーム逆転型2重差動装置の
第1実施例を示す平断面図、第2図は其パワートレイン
をスケルトンで示す平面概略図、第3図は、其プラネタ
リキャリヤの側面図、第4図は、プラネタリキャリヤ反
共ウオームの構成を示す断面図、第5図は、左右減速歯
車上のピニオン、左右ベベルギヤの配置図、第6図は、
其第2実施例のパワートレインをスケルトンで示す平面
概略図、第7図は、2ウオ一ム正転型2重差動装置用の
プラネタリキャリヤ***ウオームの構成を示す断面図及
第8図は、4ウオ一ム正転型2重差動装置用のプラネタ
リキャリヤ***ウオームの構成を示す断面図を夫々示す
。
符号の説明
78 左前車輪
79 右前車輪
81 取付金具プレートFIG. 1 is a plan sectional view showing a first embodiment of the four-worm reversing type double differential of the present invention, FIG. 2 is a plan schematic view showing its power train in skeleton form, and FIG. 3 is its planetary A side view of the carrier, FIG. 4 is a sectional view showing the configuration of the planetary carrier anti-common worm, FIG. 5 is a layout diagram of pinions on the left and right reduction gears, and left and right bevel gears, and FIG.
FIG. 7 is a plan view schematically showing the power train of the second embodiment as a skeleton; FIG. 7 is a cross-sectional view showing the configuration of a planetary carrier anti-common worm for a two-worm normal rotation type double differential; and FIG. , sectional views showing the configuration of a planetary carrier anti-common worm for a four-worm normal rotation type double differential device, respectively. Explanation of symbols 78 Left front wheel 79 Right front wheel 81 Mounting bracket plate
Claims (5)
間で差動回転する2重差動装置の前ウォーム歯車の回転
を前ウォームと同体の伝動ギヤ、前内ウォーム軸上のア
イドラーギヤ、プラネタリキヤリヤ上の中間ギヤ、及後
内ウォームと同体の伝動ギヤを介して後内ウォーム歯車
を連動回転し、前内ウォーム歯車の回転を前内ウォーム
と同体の伝動ギヤ、プラネタリキヤリヤ上の中間ギヤ、
後内ウォーム軸上のアイドラーギヤ及後ウォームと同体
の伝動ギヤを介して、後ウォーム歯車を連動回転するこ
とを特徴とする、常時四輪駆動装置。(1) Rotation of the front worm gear of a double differential device that differentially rotates between the left front axle and the right rear axle, and between the right front axle and the left rear axle is controlled by a transmission gear that is the same as the front worm, and on the front inner worm shaft. The rear inner worm gear is interlocked and rotated via the idler gear on the planetary carrier, the intermediate gear on the planetary carrier, and the transmission gear that is integrated with the rear inner worm. intermediate gear on carrier,
A constant four-wheel drive device characterized in that a rear worm gear is rotated in conjunction with an idler gear on a rear inner worm shaft and a transmission gear integral with the rear worm.
用して、Y字型のパワートレインを形成したことを特徴
とするエンジン縦置車用、特許請求範囲第1項記載の常
時四輪駆動装置。(2) A vehicle with a vertical engine, characterized in that a Y-shaped power train is formed using the double differential device as set forth in claim 1, as described in claim 1. permanent four-wheel drive.
を左右ベベルギヤ、平行に一定間隔を置いて設けられた
左右軸、左右ドライブギヤを介して、左右後車軸に直結
する左右減速歯車を連動させる事を特徴とする特許請求
範囲第1項記載の常時四輪駆動装置。(3) The rotation of the front and rear pinions installed at a constant interval is linked to the left and right reduction gears directly connected to the left and right rear axles via the left and right bevel gears, the left and right shafts installed in parallel at a constant interval, and the left and right drive gears. A constant four-wheel drive system according to claim 1, characterized in that the constant four-wheel drive system is configured to:
ギヤ、中間ギヤ及前内ウォームと同体の伝動ギヤを介し
て、前内ウォーム歯車へ連動回転する事を特徴とする特
許請求範囲第1項記載の常時四輪駆動装置。(4) The front worm gear is rotated in conjunction with the front inner worm gear through a transmission gear integral with the front worm, an intermediate gear, and a transmission gear integral with the front inner worm. Continuous four-wheel drive system as described in section.
ギヤ、前内及後内ウォーム軸上のアイドラーギヤ、中間
ギヤ及後ウォームと同体の伝動ギヤを介して、後ウォー
ム歯車へ連動回転し、前内ウォーム歯車の回転を前内ウ
ォームと同体の伝動ギヤ、中間ギヤ、後内ウォームと同
体の伝動ギヤを介して、後内ウォーム歯車へ連動回転す
る事を特徴とする特許請求範囲第1項記載の常時四輪駆
動装置。(5) The rotation of the front worm gear is linked to the rear worm gear via a transmission gear that is integrated with the front worm, an idler gear on the front inner and rear worm shafts, an intermediate gear, and a transmission gear that is integrated with the rear worm. Claim 1, characterized in that the front inner worm gear is rotated in conjunction with the rear inner worm gear via a transmission gear integral with the front inner worm, an intermediate gear, and a transmission gear integral with the rear inner worm. Continuous four-wheel drive system as described in section.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP8989987A JPS63258222A (en) | 1987-04-14 | 1987-04-14 | Regular four-wheel driving system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP8989987A JPS63258222A (en) | 1987-04-14 | 1987-04-14 | Regular four-wheel driving system |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS63258222A true JPS63258222A (en) | 1988-10-25 |
Family
ID=13983581
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP8989987A Pending JPS63258222A (en) | 1987-04-14 | 1987-04-14 | Regular four-wheel driving system |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS63258222A (en) |
-
1987
- 1987-04-14 JP JP8989987A patent/JPS63258222A/en active Pending
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