JPH1082455A - Driving shiftable reduction gears for automobile - Google Patents

Driving shiftable reduction gears for automobile

Info

Publication number
JPH1082455A
JPH1082455A JP9267633A JP26763397A JPH1082455A JP H1082455 A JPH1082455 A JP H1082455A JP 9267633 A JP9267633 A JP 9267633A JP 26763397 A JP26763397 A JP 26763397A JP H1082455 A JPH1082455 A JP H1082455A
Authority
JP
Japan
Prior art keywords
output member
input shaft
shift
gear
teeth
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
Application number
JP9267633A
Other languages
Japanese (ja)
Inventor
Lipichtz Klaus
クラウス・リピツチユ
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Steyr Daimler Puch AG
Magna Steyr Fahrzeugtechnik GmbH and Co KG
Original Assignee
Steyr Daimler Puch AG
Steyr Daimler Puch Fahrzeugtechnik AG and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Steyr Daimler Puch AG, Steyr Daimler Puch Fahrzeugtechnik AG and Co KG filed Critical Steyr Daimler Puch AG
Publication of JPH1082455A publication Critical patent/JPH1082455A/en
Pending legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46Gearings having only two central gears, connected by orbital gears
    • F16H3/48Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/54Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60KARRANGEMENT 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
    • B60K17/00Arrangement or mounting of transmissions in vehicles
    • B60K17/04Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B60K17/08Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60KARRANGEMENT 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
    • B60K17/00Arrangement or mounting of transmissions in vehicles
    • B60K17/34Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/344Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
    • B60K17/346Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
    • B60K17/3467Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear combined with a change speed gearing, e.g. range gear

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)
  • Arrangement Of Transmissions (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide reduction gears with only minimum frictional loss, wear, noise and heating generated in an on-road running speed change stage. SOLUTION: Shiftable reduction gears consists of a case 1, an input shaft 4, an output member 6, planetary gears 7 and a shift sleeve 8 movable on the output member 6 and always connected to the output member 6. The planetary gears 7 consist of an internal tooth ring gear 10 fixedly connected to the case 1, a sun gear 11 on the input shaft 4, and an epicyclic carrier 13 with a first connecting tooth 17. In order to receive only minimum loss in a road traveling speed change stage, then sun gear 11 is rotatably supported on the input shaft 4 and has a third connecting tooth 19, and a shift boss 5 with a fourth connecting tooth 21 is connected out of relative rotation to the input shaft 4. In addition, a shift ring 22 has a fifth connecting tooth 23 and is rotatably guided in the shift sleeve 8.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【0001】[0001]

【産業上の利用分野】本発明は、減速歯車装置がケー
ス、入力軸、出力部材、遊星歯車装置、及び出力部材上
を移動可能でこれに常に連結されているシフトスリーブ
を含み、遊星歯車装置が、ケースに固定的に結合され
ている内歯環状歯車と、入力軸上にある太陽歯車と、第
1の連結歯を持つ遊星キヤリヤとから構成され、第1の
連結歯がシフトスリーブ上の第2の連結歯に連結可能で
ある、自動車の駆動用のシフト可能な減速歯車装置に関
する。
BACKGROUND OF THE INVENTION The present invention relates to a planetary gear system in which a reduction gear unit includes a case, an input shaft, an output member, a planetary gear unit, and a shift sleeve movable on the output member and always connected thereto. Comprises a ring gear internally fixedly connected to the case, a sun gear on the input shaft, and a planet carrier with first connecting teeth, the first connecting teeth on the shift sleeve. The present invention relates to a shiftable reduction gear device for driving an automobile, which is connectable to a second connection tooth.

【0002】[0002]

【従来の技術】このような減速歯車装置は、全輪駆動車
両の動力伝達系において、種々の配置即ち縦置き又は横
置きで、また後に続く動力伝達系の素子の種々の配置で
使用される。その際ケースに固定した内歯環状歯車は、
小さい所要空間、費用の少ない構造及び簡単な組立てに
寄与する。大きくかつ重い内歯環状歯車は回転しないの
で、高速で回転する慣性質量も小さくなる。
2. Description of the Related Art Such reduction gears are used in power transmission systems of all-wheel drive vehicles in various arrangements, i.e., vertically or horizontally, and in various arrangements of the elements of the power transmission system that follow. . At that time, the ring gear fixed to the case,
It contributes to small space requirements, low cost structure and simple assembly. Since the large and heavy ring gear does not rotate, the inertial mass rotating at high speed is also reduced.

【0003】最初にあげた種類の減速歯車装置は欧州特
許公告第202951号明細書から公知である。そこで
は太陽歯車が入力軸に固定的に結合され、シフトスリー
ブにより直接出力部材に連結され、それにより高速の路
上走行変速段が得られる。しかしその際遊星歯車が太陽
歯車上を転動し、遊星キヤリヤも回転させる。これは望
ましくない。なぜならば、それにより、最も多くの時間
を使用する変速段において(しかも純粋な野外走行車は
路上走行変速段において最大の区間を高い速度で走行す
る)、大きい摩擦損失、摩耗、騒音及び加熱が起こるか
らである。最初にあげた種類の他の公知の減速歯車装
置、New Venture Gearsの形式NVG
249でも、状況は同じである。
A reduction gear train of the type mentioned at the beginning is known from EP-A-202 951. There, a sun gear is fixedly connected to the input shaft and is connected directly to the output member by means of a shift sleeve, whereby a high road speed is obtained. However, the planet gears then roll on the sun gear, causing the planet carrier to also rotate. This is undesirable. Because, at the gears that use the most time (and pure outdoor vehicles travel at the highest speeds in roadway gears at the highest speeds), large friction losses, wear, noise and heating are caused. Because it will happen. Another known reduction gearing of the type mentioned at the outset, type NVG of the New Venture Gears
At 249, the situation is the same.

【0004】[0004]

【発明が解決しようとする課題】従つて本発明の目的
は、最初にあげた種類の減速歯車装置を改良して、路上
走行変速段で最小の摩擦損傷、摩耗、騒音及び加熱しか
起こらないようにすることである。
SUMMARY OF THE INVENTION It is therefore an object of the present invention to improve a reduction gearing of the type mentioned at the outset so that only minimal friction damage, wear, noise and heating occur at road speeds. It is to be.

【0005】[0005]

【課題を解決するための手段】このため本発明によれ
ば、 a)太陽歯車が入力軸上に自由に回転可能に支持され、
かつ第3の連結歯を持ち、 b)シフトボスが第4の連結歯を持ち、かつ入方軸に相
対回転しないように結合され、 c)シフトリングが第5の連結歯を持ち、かつシフトス
リーブ内に回転可能に案内されている。
According to the present invention, there is provided: a) a sun gear is rotatably supported on an input shaft;
And b) the shift boss has fourth connection teeth and is coupled so as not to rotate relative to the incoming shaft; c) the shift ring has fifth connection teeth, and has a shift sleeve. It is rotatably guided inside.

【0006】特徴a)は、高速の変速段で遊星歯車装置
を停止させ、トルクなしにするための前提条件を、それ
から生ずるすべての利点を伴つて、与える。特徴b)に
より入力軸に常に連結されるシフトボスは、特徴c)に
よるシフトリングにより直接出力部材に連結され、これ
はシフトリングの自由な回転可能性によつてのみ可能で
ある。しかし路上走行変速段ではシフトスリーブが同じ
回転数で回転し、従つて相対回転が行われないので、摩
耗は起こらない。野外走行変速段でも、野外走行変速段
の減速比に応じて、相対回転数は僅かである。シフトリ
ングはシフトスリーブ内に案内されているので、ただ1
つの操作機構で間に合う。
[0006] Feature a) provides a prerequisite for stopping the planetary gear set at high gear and without torque, with all the advantages that result therefrom. The shift boss, which is always connected to the input shaft according to feature b), is directly connected to the output member by the shift ring according to feature c), which is only possible due to the free rotation of the shift ring. However, at the speed on road, the shift sleeve rotates at the same speed and therefore does not rotate relative to each other, so that no wear occurs. Even at the outdoor travel speed, the relative rotational speed is small according to the reduction ratio of the outdoor travel speed. The shift ring is guided in the shift sleeve, so only one
Makes time with one operating mechanism.

【0007】好ましい実施態様では、移動可能なシフト
スリーブと出力部材が、第6の連結歯及び外歯である第
7の連結歯により連結され、第4の連結歯が第7の連結
歯と同じ断面を持つている(請求項2)。こうしてこれ
らの連結歯は同じ寸法を持ち、それにより製造が著しく
安価になり、シフトスリーブが一方では出力部材上に他
方ではシフトリングを介して案内されるので、シフトス
リーブは付加的な軸受なしに正確に案内されている。
In a preferred embodiment, the movable shift sleeve and the output member are connected by a sixth connecting tooth and a seventh connecting tooth which is an external tooth, and the fourth connecting tooth is the same as the seventh connecting tooth. It has a cross section (claim 2). In this way, the connecting teeth have the same dimensions, which makes the manufacture significantly less expensive and the shift sleeve is guided on the one hand on the output member and on the other hand via the shift ring, so that the shift sleeve can be used without additional bearings. Guided correctly.

【0008】更に連結歯の適当な軸線方向位置ぎめによ
り、シフトの際すべての連結歯が同時にかみ合わないよ
うにすることができ、それによりシフト過程が2つの運
動段階で快適に行われる。これは、路上走行変速段から
野外走行変速段への切換えの際遊星歯車装置全体が路上
走行変速段でなお自由に回転可能でかつトルクなしであ
ることによつても、助長される。
In addition, a suitable axial positioning of the connecting teeth ensures that all the connecting teeth do not engage at the same time during the shifting, so that the shifting process takes place comfortably in two phases of movement. This is also facilitated by the fact that the entire planetary gear set is still rotatable and torque-free at the road speed when switching from the road speed to the outdoor speed.

【0009】第3の連結歯が太陽歯車のカラー上の外歯
であり、第7の連結歯と同じ断面を持つている(請求項
3)と、入力軸上における太陽歯車の一層の簡単化及び
案内長の増大が行われる。
If the third connecting tooth is an external tooth on the collar of the sun gear and has the same cross section as the seventh connecting tooth (claim 3), the sun gear can be further simplified on the input shaft. And the guide length is increased.

【0010】減速歯車装置は多様な構成で使用すること
ができる。それとは無関係に、出力部材が差動歯車装置
の駆動部材に伝動結合されている(請求項4)と、構造
的な簡単化が行われる。傘歯車の差動歯車装置を使用す
る場合、この簡単化は、出力部材が差動歯車ケースの一
部である(請求項5)と、特に大きい。
The reduction gear can be used in a variety of configurations. Independently, a structural simplification results if the output member is drive-coupled to the drive member of the differential gearing (claim 4). This simplification is particularly significant when using a bevel gear differential gearing, provided that the output member is part of a differential gear case (claim 5).

【0011】中央差動歯車装置従つて動力伝達系の縦配
置では、入力軸及び出力部材が中空軸であり、これらの
中空軸の内部空間に、差動歯車装置により駆動される軸
が収容されている(請求項6)と、特に有利な配置が行
われる。
In the vertical arrangement of the power transmission system, the input shaft and the output member are hollow shafts, and the shaft driven by the differential gear device is housed in the internal space of these hollow shafts. (Claim 6) provides a particularly advantageous arrangement.

【0012】[0012]

【実施例】ただ1つの図に示されている実施例につい
て、本発明を以下に説明する。
BRIEF DESCRIPTION OF THE DRAWINGS The invention is described below with reference to an embodiment shown in only one figure.

【0013】シフト可能な減速歯車装置のケース1は、
固有のケース又はもつと大きいケースの一部であつても
よい。図の左側でケース1を閉鎖するケース蓋2は、特
別な場合中空軸である入力軸4の軸受3を収容してい
る。図の右側でケース1は切断されているので、他方の
軸受は見えない。入力軸4上にはシフトボス5がキー止
めされている。出力部材6は入力軸4に対して同心的に
設けられている。入力軸4は遊星歯車装置7により包囲
されている。この遊星歯車装置7は、シフトフオーク9
(破線)及びシフトスリーブ8により、低速の変速段
(野外走行変速段)と高速の変速段(路上走行変速段)
との間で往復シフトされることができる。
The case 1 of the shiftable reduction gear device comprises:
It may be a unique case or part of a larger case. The case lid 2, which closes the case 1 on the left side of the figure, houses the bearing 3 of the input shaft 4, which is a special case hollow shaft. Since the case 1 is cut off on the right side of the figure, the other bearing is not visible. A shift boss 5 is keyed on the input shaft 4. The output member 6 is provided concentrically with respect to the input shaft 4. The input shaft 4 is surrounded by a planetary gear set 7. This planetary gear set 7 has a shift fork 9
(Dashed line) and the shift sleeve 8, the low speed (outdoor running speed) and the high speed (road running speed).
Can be shifted back and forth.

【0014】遊星歯車装置7は、ケース1内に固定的に
設けられる円歯環状歯車10と、針軸受12により入力
軸4上に支持される太陽歯車11と、遊星キヤリヤ13
とから成つている。遊星キヤリヤ13は、遊星歯車15
を回転可能に支持する多数の遊星軸14を持ち、内歯と
して構成される第1の連結歯17を持つカラー板16に
終つている。
The planetary gear device 7 includes an annular gear 10 fixedly provided in the case 1, a sun gear 11 supported on the input shaft 4 by a needle bearing 12, and a planet carrier 13.
And consists of The planet carrier 13 includes a planetary gear 15.
Has a number of planetary shafts 14 rotatably supporting and terminates in a collar plate 16 having first connecting teeth 17 configured as internal teeth.

【0015】この第1の連結歯17は、シフトスリーブ
8の外歯として構成される第2の連結歯18と共同作用
する。太陽歯車11は第3の連結歯19を持つカラー2
0を持ち、それに続くシフトボス5は、第3の連結歯1
9と同じ断面を持つ外歯として構成される第4の連結歯
21を持つている。
The first connecting teeth 17 cooperate with second connecting teeth 18 which are configured as external teeth of the shift sleeve 8. The sun gear 11 is a collar 2 having third connecting teeth 19
0, and the shift boss 5 following the third connecting tooth 1
It has fourth connecting teeth 21 configured as external teeth having the same cross section as 9.

【0016】シフトスリーブ8内にはシフトリング22
が自由に回転可能に案内されている。シフトリング22
は内歯として構成される第5の連結歯23を持ち、軸線
方向において止め輪25により止められる案内輪24に
よつて両側をシフトスリーブ8内に案内されて、シフト
スリーブ8の移動の際一緒に移動せしめられるが、シフ
トスリーブ8とは無関係に回転可能である。
A shift ring 22 is provided in the shift sleeve 8.
Are guided so as to be freely rotatable. Shift ring 22
Have fifth connecting teeth 23, which are formed as internal teeth, which are guided on both sides into the shift sleeve 8 by guide wheels 24 which are stopped in the axial direction by retaining rings 25 and which , But can be rotated independently of the shift sleeve 8.

【0017】更にシフトスリーブ8は第6の連結歯26
を持ち、シフトスリーブ8が移動可能であつても、この
第6の連結歯26が出力部材6のシフトスリーブ8と常
に共同作用する。シフトスリーブ8は、第6の連結歯2
6と第7の連結歯27の共同作用によつて正確に中心に
案内される。
Further, the shift sleeve 8 has a sixth connecting tooth 26.
And the sixth connecting teeth 26 always cooperate with the shift sleeve 8 of the output member 6 even if the shift sleeve 8 is movable. The shift sleeve 8 is connected to the sixth connecting teeth 2.
It is guided exactly to the center by the joint action of the sixth and seventh connecting teeth 27.

【0018】図示した実施例では、出力部材6は、全体
を30で示す差動歯車装置の駆動部材としての差動歯車
ケース31と同じ部分である。差動歯車ケース31は公
知のように差動傘歯車32と1つだけ見える従動傘歯車
33とを収容している。従動傘歯車33は、減速歯車装
置の組込みに応じて車軸駆動軸又は車輪駆動軸であつて
もよい軸34に連結されている。
In the illustrated embodiment, the output member 6 is the same as the differential gear case 31 as a driving member of the differential gear device, which is indicated as a whole. As is well known, the differential gear case 31 houses a differential bevel gear 32 and a driven bevel gear 33 that can be seen only once. The driven bevel gear 33 is connected to a shaft 34 which may be an axle drive shaft or a wheel drive shaft depending on the installation of the reduction gear device.

【0019】本発明による減速歯車装置の動作は次の通
りである。路上走行変速段(図の下半分)では、入力軸
4がシフトボス5及びシフトリング22を介して出力部
材6を駆動する。その際シフトリング22の第5の連結
歯23はシフトボス5の第4の連結歯21へかみ合うと
共に、出力部材6の第7の連結歯27にもかみ合う。シ
フトスリーブ8も第6の連結歯26及び第7の連結歯2
7を介して同じ回転数で回転されるので、シフトスリー
ブ8とシフトリング22との間に相対回転はなく、従つ
て摩耗も損失もない。シフトスリーブ8は、第7の連結
歯27とは反対の側にあるシフトスリーブ8の端乱で
も、シフトリング22を介して入力軸4に対し心出しさ
れる。この位置で遊星キヤリヤ13の第1の連結歯17
はシフトスリーブ8の第2の連結歯18にかみ合つてい
ないので、遊星キヤリヤ13は静止し、ケース1に固定
の内歯環状歯車10のため、遊星歯車15及び太陽歯車
11も静止している。従つて遊星歯車装置7は損失を生
じない。
The operation of the reduction gear device according to the present invention is as follows. At the road speed (lower half in the figure), the input shaft 4 drives the output member 6 via the shift boss 5 and the shift ring 22. At this time, the fifth connecting teeth 23 of the shift ring 22 engage with the fourth connecting teeth 21 of the shift boss 5 and also engage with the seventh connecting teeth 27 of the output member 6. The shift sleeve 8 also has the sixth connecting teeth 26 and the seventh connecting teeth 2.
Since the gear is rotated at the same rotational speed via the shaft 7, there is no relative rotation between the shift sleeve 8 and the shift ring 22, and therefore there is no wear or loss. The shift sleeve 8 is centered with respect to the input shaft 4 via the shift ring 22 even when the end of the shift sleeve 8 on the side opposite to the seventh connecting teeth 27 is disturbed. In this position, the first connecting teeth 17 of the planet carrier 13
Are not engaged with the second connecting teeth 18 of the shift sleeve 8, the planetary carrier 13 is stationary, and the planetary gear 15 and the sun gear 11 are stationary because of the internal gear 10 fixed to the case 1. I have. Accordingly, the planetary gear set 7 does not cause any loss.

【0020】さて路上走行変速段から中立位置を経て野
外走行変速段(図の上半分)へシフトされ、そのために
シフトスリーブ8が図で左方へ移動せしめられると、ま
ずシフトリング22の第5の連結歯23が出力部材6の
シフトスリーブ8から外れる。減速歯車装置は中立位置
にあり、シフトリング22がシフトスリーブ8内で自由
に回転できるので、減速歯車装置はトルクを伝達しな
い。それからシフトスリーブ8が更に左方へ移動せしめ
られると、まずシフトスリーブ8の第2の連結歯18が
遊星キヤリヤ13の第1の連結歯17へかみ合う。遊星
キヤリヤ13もまだ自由に回転可能なので、両方の連結
歯は問題なくかみ合つている。シフトスリーブ8の引続
く移動の際始めて、シフトリング22の第5の連結歯2
3も太陽歯車11の第3の連結歯19にかみ合う。従つ
て切換えは2段で行われる。
When the shift speed is shifted from the road speed to the outdoor speed (the upper half in the figure) through the neutral position, and the shift sleeve 8 is moved to the left in the figure, the fifth shift ring 22 Are disengaged from the shift sleeve 8 of the output member 6. Since the reduction gear is in the neutral position and the shift ring 22 can rotate freely within the shift sleeve 8, the reduction gear does not transmit torque. Then, when the shift sleeve 8 is further moved to the left, first, the second connecting teeth 18 of the shift sleeve 8 engage with the first connecting teeth 17 of the planet carrier 13. Since the planet carrier 13 is still freely rotatable, the two connecting teeth engage without problems. Only after a subsequent movement of the shift sleeve 8 does the fifth connecting tooth 2 of the shift ring 22
3 also meshes with the third connecting teeth 19 of the sun gear 11. Therefore, the switching is performed in two stages.

【0021】野外走行変速段では動力の流れは次の通り
である。まず入力軸4はシフトボス5及びシフトリング
22を介して太陽歯車11を駆動する。円歯環状歯車1
0が静止しているため、遊星キヤリヤ13の回転数は入
力軸4の回転数より小さい。遊星キヤリヤ13は第1の
連結歯17及び第2の連結歯18を介してシフトスリー
ブ8を駆動し、シフトスリーブ8は第6の連結歯26及
び第7の連結歯27を介して出力部材6を駆動する。そ
の際シフトリング22とシフトスリーブ8との間に相対
回転が存在するが、その値は入力軸4の回転数と出力部
材6の回転数との差であるにすぎない。
At the outdoor speed stage, the flow of power is as follows. First, the input shaft 4 drives the sun gear 11 via the shift boss 5 and the shift ring 22. Ring gear 1
Since 0 is stationary, the rotation speed of the planet carrier 13 is smaller than the rotation speed of the input shaft 4. The planet carrier 13 drives the shift sleeve 8 via the first connecting teeth 17 and the second connecting teeth 18, and the shift sleeve 8 is connected via the sixth connecting teeth 26 and the seventh connecting teeth 27 to the output member 6. Drive. At that time, there is a relative rotation between the shift ring 22 and the shift sleeve 8, but the value is merely a difference between the rotation speed of the input shaft 4 and the rotation speed of the output member 6.

【図面の簡単な説明】[Brief description of the drawings]

【図1】本発明による減速歯車装置の縦断面図で、中心
軸線より上では野外走行変速段に相当する低速の変速段
が示され、その下では路上走行変速段に相当する高速の
変速段が示されている。
FIG. 1 is a longitudinal sectional view of a reduction gear device according to the present invention, in which a lower gear corresponding to an outdoor traveling gear is shown above a center axis, and a high gear corresponding to a road traveling gear below the center axis. It is shown.

【符号の説明】[Explanation of symbols]

1 ケース 4 入力軸 5 シフトボス 6 出力部材 7 遊星歯車装置 8 シフトスリーブ 10 内歯環状歯車 11 太陽歯車 13 遊星キヤリヤ 17,18,19,21,23 連結歯 22 シフトリング DESCRIPTION OF SYMBOLS 1 Case 4 Input shaft 5 Shift boss 6 Output member 7 Planetary gear device 8 Shift sleeve 10 Internal gear ring gear 11 Sun gear 13 Planet carrier 17, 18, 19, 21, 23 Connecting tooth 22 Shift ring

フロントページの続き (72)発明者 クラウス・リピツチユ オーストリア国グラーツ・コシヤツトガツ セ17/4/30Continuation of the front page (72) Inventor Klaus Lipitsuille Graz-Kosiat-Gatse, Austria 17/4/30

Claims (6)

【特許請求の範囲】[Claims] 【請求項1】 減速歯車装置がケース(1)、入方軸
(4)、出力部材(6)、遊星歯車装置(7)、及び出
力部材(6)上を移動可能でこれに常に連結されている
シフトスリーブ(8)を含み、 遊星歯車装置(7)が、ケース(1)に固定的に結合さ
れている内歯環状歯車(10)と、入力軸(4)上にあ
る太陽歯車(11)と、第1の連結歯(17)を持つ遊
星キヤリヤ(13)とから構成され、第1の連結歯(1
7)がシフトスリーブ(8)上の第2の連結歯(18)
に連結可能であるものにおいて、 a)太陽歯車(11)が入力軸(4)上に自由に回転可
能に支持され、かつ第3の連結歯(19)を持ち、 b)シフトボス(5)が第4の連結歯(21)を持ち、
かつ入方軸(4)に相対回転しないように結合され、 c)シフトリング(22)が第5の連結歯(23)を持
ち、かつシフトスリーブ(8)内に回転可能に案内され
ていることを特徴とする、自動車の駆動用のシフト可能
な減速歯車装置。
1. A reduction gear unit is movable on a case (1), an input shaft (4), an output member (6), a planetary gear unit (7), and an output member (6) and is always connected thereto. A planetary gear set (7) fixedly connected to the case (1) and a sun gear (10) on the input shaft (4). 11) and a planet carrier (13) having first connecting teeth (17), and the first connecting teeth (1
7) is the second connecting tooth (18) on the shift sleeve (8).
A) a sun gear (11) is rotatably supported on an input shaft (4) and has third connecting teeth (19); b) a shift boss (5) Having a fourth connecting tooth (21),
And the rotation ring (22) has fifth connecting teeth (23) and is rotatably guided in the shift sleeve (8). A shiftable reduction gear for driving a motor vehicle.
【請求項2】 移動可能なシフトスリーブ(8)と出力
部材(6)が、第6の連結歯(26)及び外歯である第
7の連結歯(27)により連結され、第4の連結歯(2
1)が第7の連結歯(27)と同じ断面を持つているこ
とを特徴とする、請求項1に記載のシフト可能な減速歯
車装置。
2. The movable shift sleeve (8) and the output member (6) are connected by a sixth connecting tooth (26) and a seventh connecting tooth (27), which is an external tooth, and a fourth connection. Teeth (2
2. The shiftable reduction gear according to claim 1, wherein 1) has the same cross section as the seventh connecting tooth.
【請求項3】 第3の連結歯(19)が太陽歯車(1
1)のカラー(20)上の外歯であり、第7の連結歯
(27)と同じ断面を持つていることを特徴とする、請
求項2に記載のシフト可能な減速歯車装置。
3. A sun gear (1) wherein a third connecting tooth (19) is provided.
3. The shiftable reduction gear device according to claim 2, wherein the external teeth on the collar (20) of 1) have the same cross section as the seventh connecting teeth (27).
【請求項4】 出力部材(6)が差動歯車装置(30)
の駆動部材(31)に伝動結合されていることを特徴と
する、請求項1に記載のシフト可能な減速歯車装置。
The output member (6) is a differential gear device (30).
2. The shiftable reduction gear set according to claim 1, wherein the transmission is geared to the drive member.
【請求項5】 出力部材(6)が差動歯車ケース(3
1)の一部であることを特徴とする、請求項4に記載の
シフト可能な減速歯車装置。
5. The output member (6) is a differential gear case (3).
5. The shiftable reduction gear according to claim 4, wherein the reduction gear is part of 1).
【請求項6】 入力軸(4)及び出力部材(6)が中空
軸であり、これらの中空軸の内部空間に、差動歯車装置
(30)により駆動される軸(34)が収容されている
ことを特徴とする、請求項5に記載のシフト可能な減速
歯車装置。
6. An input shaft (4) and an output member (6) are hollow shafts, and a shaft (34) driven by a differential gear device (30) is housed in an inner space of these hollow shafts. The shiftable reduction gear device according to claim 5, wherein:
JP9267633A 1996-08-28 1997-08-26 Driving shiftable reduction gears for automobile Pending JPH1082455A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19634775.0 1996-08-28
DE1996134775 DE19634775C1 (en) 1996-08-28 1996-08-28 Simple planetary gearbox

Publications (1)

Publication Number Publication Date
JPH1082455A true JPH1082455A (en) 1998-03-31

Family

ID=7803924

Family Applications (1)

Application Number Title Priority Date Filing Date
JP9267633A Pending JPH1082455A (en) 1996-08-28 1997-08-26 Driving shiftable reduction gears for automobile

Country Status (2)

Country Link
JP (1) JPH1082455A (en)
DE (1) DE19634775C1 (en)

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61270562A (en) * 1985-05-24 1986-11-29 Toyota Motor Corp Auxiliary speed change gear
US5106351A (en) * 1991-04-23 1992-04-21 New Venture Gear, Inc. Transfer case limited slip planetary differential

Also Published As

Publication number Publication date
DE19634775C1 (en) 1998-05-07

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