JPS63258222A - Regular four-wheel driving system - Google Patents

Abstract

PURPOSE:To form each diameter into the same and aim at the promotion of lightweightiness and miniaturization as a whole by increasing two sets of transmission spur gears to a dual differential gear. CONSTITUTION:Intermediate gears 9 and 12 on a planetary carrier 2 are used for part of an interlocking gear of a worm in a dual differential gear 1, and this planetary carrier 2 is rotated by a main shaft 17 via a planetary carrier disc 18, whereby each interlocking gear will do in the same diameter as a known toe center differential gear, thus an outer diameter of the planetary carrier 2 is in no case increased at all.

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.

【図面の簡単な説明】[Brief explanation of the drawing]

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)

【特許請求の範囲】[Claims] （１）左前車軸と右後車軸及、右前車軸と左後車軸との
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. （２）特許請求の範囲第１項に記載の２重差動装置を使
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. （３）一定間隔を置いて設けられた前後ピニオンの回転
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: （４）前ウォーム歯車の回転を前ウォームと同体の伝動
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. （５）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.