JPH01238719A - Multiple disc clutch - Google Patents
Multiple disc clutchInfo
- Publication number
- JPH01238719A JPH01238719A JP63063673A JP6367388A JPH01238719A JP H01238719 A JPH01238719 A JP H01238719A JP 63063673 A JP63063673 A JP 63063673A JP 6367388 A JP6367388 A JP 6367388A JP H01238719 A JPH01238719 A JP H01238719A
- Authority
- JP
- Japan
- Prior art keywords
- clutch
- motor
- friction
- hollow shaft
- case
- 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
- 238000006243 chemical reaction Methods 0.000 claims description 7
- 230000002159 abnormal effect Effects 0.000 abstract description 4
- 230000004907 flux Effects 0.000 abstract description 4
- 229910000831 Steel Inorganic materials 0.000 abstract description 3
- 239000010959 steel Substances 0.000 abstract description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 8
- 230000005540 biological transmission Effects 0.000 description 4
- 229910052742 iron Inorganic materials 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 229910045601 alloy Inorganic materials 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
-
- 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
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
- B60K17/346—Arrangement 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
- B60K17/3462—Arrangement 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 with means for changing distribution of torque between front and rear wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D28/00—Electrically-actuated clutches
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/295—Arrangements for suppressing or influencing the differential action, e.g. locking devices using multiple means for force boosting
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
- F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/06—Means for converting reciprocating motion into rotary motion or vice versa
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H2048/204—Control of arrangements for suppressing differential actions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
- F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
- F16H2048/343—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators using a rotary motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
- F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
- F16H2048/346—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators using a linear motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H48/40—Constructional details characterised by features of the rotating cases
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Power Engineering (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
- Retarders (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
【発明の詳細な説明】 し発明の目的] (産業上の利用分野) この発明は、多板クラッチに関する。[Detailed description of the invention] Purpose of invention] (Industrial application field) The present invention relates to a multi-disc clutch.
(従来の技術)
従来、締結力の調節可能な多板クラッチとしては締結と
解放および締結力の調節などを電磁石の吸引力で行う電
磁クラッチや流体圧で作動するアクチュエータの押圧力
で行うものく以下代表的に油圧式クラッチという)など
がある。(Prior art) Conventionally, multi-disc clutches with adjustable fastening force include electromagnetic clutches that use the attraction force of an electromagnet to engage and release, and adjust the fastening force using the pressing force of an actuator operated by fluid pressure. Hereinafter, the clutches are typically referred to as hydraulic clutches.
電磁クラッチは、吸引力を大きくしてクラッチの容量と
応答速度とを増すために磁束を効率よく通す摩擦板を用
いる必要があり、そのため実際上摩擦板材料としてはラ
イニングを施さない鉄板に限られる。第3図に示した、
摩擦速度■と摩擦係数μとで表される摩擦特性のグラフ
において実線で示したように鉄板の摩擦板の摩擦特性は
VがOの付近にピークがあり、このようなμの変動によ
って鳴き音や振動音が発生し易い。第3図に破線で示し
たように、摩擦特性は一般になだらかに右上りを呈する
ものが望ましい。鉄板に例えばベーパや銅系合金のライ
ニングを施した摩擦板にはこの特性を満たすものがある
がライニング層が磁束の通過を阻害するので電磁クラッ
チに用いることはできない。また、油圧式クラッチにお
いては、オイルポンプ等の油圧発生源、導管、アクチュ
エータ等が必要となり、装置の部品点数の増加、大型化
、等が問題となる。Electromagnetic clutches need to use friction plates that efficiently pass magnetic flux in order to increase the attractive force and increase the clutch capacity and response speed. Therefore, in practice, the friction plate material is limited to iron plates without lining. . As shown in Figure 3,
As shown by the solid line in the graph of the friction characteristics expressed by the friction velocity ■ and the friction coefficient μ, the friction characteristics of the iron friction plate have a peak near V = O, and such fluctuations in μ cause squealing noise. vibration noise is likely to occur. As shown by the broken line in FIG. 3, it is generally desirable that the friction characteristics exhibit a gentle upward slope to the right. There are friction plates made of iron plates lined with vapor or copper-based alloys that satisfy this characteristic, but cannot be used in electromagnetic clutches because the lining layer obstructs the passage of magnetic flux. Further, in a hydraulic clutch, a hydraulic pressure generation source such as an oil pump, a conduit, an actuator, etc. are required, which causes problems such as an increase in the number of parts and an increase in the size of the device.
(発明が解決しようとする課題)
そこで、この発明は摩擦特性のよい摩擦板を用いること
ができ、作動特性に優れるとともに部品点数の少い多板
クラッチの提供を目的とする。(Problems to be Solved by the Invention) Therefore, an object of the present invention is to provide a multi-plate clutch that can use friction plates with good friction characteristics, has excellent operating characteristics, and has a small number of parts.
[発明の構成]
(It!題を解決するための手段)
この発明の多板クラッチは、筒状のケースと、同軸上で
相対回転可能にこのケースに内装されたハブ部材と、こ
のハブ部材の外周と前記ケースの内周に各別に回転方向
に係合し交互に配置された複数枚の摩擦板とからなるク
ラッチ部と、外部制御可能なモータと、このモータの回
転力を変換して前記クラッチを押圧し締結させる変換機
構とを備えたことを特徴とする。[Structure of the Invention] (Means for Solving the Problem) The multi-disc clutch of the present invention includes a cylindrical case, a hub member housed in the case so as to be relatively rotatable on the same axis, and the hub member. a clutch portion consisting of a plurality of friction plates arranged alternately and engaged with the outer periphery of the case and the inner periphery of the case separately in the rotational direction; a motor that can be externally controlled; The present invention is characterized by comprising a conversion mechanism that presses and engages the clutch.
(作用)
変換機構はモータの回転力を方向変換してクラッチを押
圧し締結させる。モータの回転方向や電流値を外部制御
することによりクラッチの締結と解放および締結力の調
節などが行える。クラッチが締結されればケースとハブ
部材の一方からの回転入力が他方から、クラッチの締結
力の大きさに応じた割合で、出力される。(Operation) The conversion mechanism changes the direction of the rotational force of the motor to press and engage the clutch. By externally controlling the rotation direction and current value of the motor, it is possible to engage and release the clutch and adjust the engagement force. When the clutch is engaged, rotational input from one of the case and the hub member is output from the other at a rate corresponding to the magnitude of the engagement force of the clutch.
(実施例) 第1図と第2図により一実施例の説明をする。(Example) One embodiment will be explained with reference to FIG. 1 and FIG. 2.
この実施例は、第2図に小したように、四輪駆動(4W
D)車のトランスファーケースに納められたセンターデ
フの差動制限装置として用いられている。なお、以下の
説明において左右方向は第1図の左右方向であり、この
車両の前後方向に相当する。This embodiment has four-wheel drive (4W) as shown in FIG.
D) It is used as a differential limiting device for the center differential housed in a car's transfer case. In the following description, the left-right direction is the left-right direction in FIG. 1, and corresponds to the front-rear direction of the vehicle.
先ず第2図によりこの車両における動力伝達を説明する
。First, power transmission in this vehicle will be explained with reference to FIG.
エンジン1の回転はトランスミッション3で変速され出
力軸5を介してトランスファ7に伝達される。トランス
ファ7は伝達された駆動力を出力軸9を介して前輪側の
デファレンシャル装置13に、又プロペラシャフト11
を介して後輪側のデファレンシャル装置15に伝達する
。これらのデファレンシャル装置13.15は伝達され
た駆動力を各々の左右輪17,19.21.23へ差動
配分する。The rotation of the engine 1 is changed in speed by a transmission 3 and transmitted to a transfer 7 via an output shaft 5. The transfer 7 transfers the transmitted driving force to the front wheel side differential device 13 via the output shaft 9, and also to the propeller shaft 11.
The signal is transmitted to the differential device 15 on the rear wheel side. These differential devices 13.15 differentially distribute the transmitted driving force to the left and right wheels 17, 19, 21, and 23, respectively.
次に、構成を説明する。Next, the configuration will be explained.
入力軸25はベアリング27によりトランスファーケー
ス29に回転自在に支承されており、出力軸5を通じて
トランスミッション3からエンジンの駆動力を入力する
。トランスファーケース29は接合部28.30を有す
るスリーピース構成となっている。出力軸31はベアリ
ング33によりトランスファーケース29に入力軸25
と同軸上で回転自在に支承されており、プロペラシャフ
ト11を通じて後輪側のデファレンシャル装置15に駆
動力を伝達する。出力軸31の前端はラッパ状に形成さ
れ、このラッパ状の端部の内側において入力軸25と出
力軸31とはニードルベアリング35を介して相対回転
可能に接続されている。The input shaft 25 is rotatably supported by a transfer case 29 by a bearing 27, and inputs the driving force of the engine from the transmission 3 through the output shaft 5. The transfer case 29 has a three-piece construction with joints 28 and 30. The output shaft 31 is connected to the input shaft 25 to the transfer case 29 by a bearing 33.
It is rotatably supported on the same axis as the propeller shaft 11 and transmits driving force to the differential device 15 on the rear wheel side. The front end of the output shaft 31 is formed in a trumpet shape, and the input shaft 25 and the output shaft 31 are connected via a needle bearing 35 so as to be relatively rotatable inside the trumpet-shaped end.
入力軸25には中空のプーリ37が同軸状に套装されて
おり、このプーリ37はニードルベアリング39により
入力軸25に、又ベアリング41によりトランスファー
ケース29に回転自在に支承されている。トランスファ
ーケース29の車幅方向の一端には他のプーリ43がベ
アリング45゜47により回転自在に支承されている。A hollow pulley 37 is coaxially mounted on the input shaft 25, and the pulley 37 is rotatably supported by the input shaft 25 by a needle bearing 39 and by the transfer case 29 by a bearing 41. Another pulley 43 is rotatably supported at one end of the transfer case 29 in the vehicle width direction by a bearing 45°47.
プーリ37とプーリ43の各回転軸は互いに平行に配置
されている。プーリ43には出力軸9を介して前輪側の
デファレンシャル装置13に駆動力を伝達する出力軸(
図示していない)がスプライン連結されている。The rotation axes of the pulley 37 and pulley 43 are arranged parallel to each other. The pulley 43 has an output shaft (
(not shown) are connected by splines.
プーリ37,43の表面には一定ピッチの凹凸が設けら
れ、この凹凸と噛み合うタイミングベルト49がプーリ
37,43を連結している。The surfaces of the pulleys 37 and 43 are provided with unevenness at a constant pitch, and a timing belt 49 that meshes with the unevenness connects the pulleys 37 and 43.
入力軸25の後端側には遊星歯車51のキャリア53が
スプライン連結されており、プーリ37の右端部外周に
は遊星歯車51と噛み合う太陽歯車55が一体に形成さ
れている。又、出力軸31のラッパ状の端部には遊星歯
車51と噛み合う内歯車57が固定されている。このよ
うにして、遊星歯車タイプのデファレンシャル装置(セ
ンターデフ)59が構成されている。従って、入力軸2
5からのエンジンの回転駆動力はキャリア53を介し、
遊星歯車51と各々噛み合った太陽歯車55と内歯車5
7とを回転させ、プーリ37、タイミングベルト49、
プーリ43を介して前輪17゜19側に伝達され、出力
軸31を介して後輪21゜23側に伝達される。又、前
輪17.19と後輪21.23との間に生じた差動回転
は遊星歯車51の回転により吸収される。A carrier 53 of a planetary gear 51 is spline connected to the rear end of the input shaft 25, and a sun gear 55 that meshes with the planetary gear 51 is integrally formed on the outer periphery of the right end of the pulley 37. Further, an internal gear 57 that meshes with the planetary gear 51 is fixed to the trumpet-shaped end of the output shaft 31. In this way, a planetary gear type differential device (center differential) 59 is configured. Therefore, input shaft 2
The rotational driving force of the engine from 5 is transmitted through the carrier 53,
A sun gear 55 and an internal gear 5 meshing with the planetary gear 51, respectively.
7, pulley 37, timing belt 49,
It is transmitted to the front wheels 17° 19 through the pulley 43, and is transmitted to the rear wheels 21° 23 through the output shaft 31. Further, the differential rotation generated between the front wheels 17.19 and the rear wheels 21.23 is absorbed by the rotation of the planetary gear 51.
トランスファーケース29の内部にはデファレンシャル
装置59の差動制限装置として機能するこの発明の多板
クラッチ61が配置されている。A multi-plate clutch 61 of the present invention, which functions as a differential limiting device for the differential device 59, is disposed inside the transfer case 29.
電気式多板クラッチ61はクラッチ部63とモータ65
と変換機構であるボールねじ67とを備えている。The electric multi-disc clutch 61 includes a clutch section 63 and a motor 65.
and a ball screw 67 which is a conversion mechanism.
クラッチ部63は円筒状のケース69とハブ部材71お
よびケース69の内周面に回転方向に係合した摩擦板7
3とハブ部材71の外周面に回転方向に係合した摩擦板
75とこれらの摩擦板73゜75の左右両側に配置され
た押圧板7v、79とからなっている。そして、ケース
69は太陽歯車55に係合しストッパリング70でスラ
スト方向に位置決めされ、ハブ部材71は出力軸31の
ラッパ状の外周部に溶接されている。これらの摩擦板7
3.75はいずれも鉄板の両面にペーパーライニング等
を施したものを用いた。The clutch portion 63 includes a cylindrical case 69, a hub member 71, and a friction plate 7 that engages with the inner peripheral surface of the case 69 in the rotation direction.
3, a friction plate 75 engaged with the outer peripheral surface of the hub member 71 in the rotational direction, and pressing plates 7v and 79 arranged on both sides of the friction plates 73 and 75. The case 69 is engaged with the sun gear 55 and positioned in the thrust direction by a stopper ring 70, and the hub member 71 is welded to the trumpet-shaped outer circumference of the output shaft 31. These friction plates 7
3.75 used iron plates with paper lining on both sides.
モータ65はそのステータ81のヨーク83をトランス
ファーケース29にボルト85で固定されている。ヨー
ク83はステータ81を保持する外側の円筒部と出力軸
31に套装する内側円筒部87を有する2重円筒状にな
っており、内側円筒部87は出力軸31の入力軸25と
の接続部をベアリング89により回転自在に支承してい
る。The motor 65 has a yoke 83 of a stator 81 fixed to the transfer case 29 with bolts 85. The yoke 83 has a double cylindrical shape, having an outer cylindrical part that holds the stator 81 and an inner cylindrical part 87 that encases the output shaft 31. The inner cylindrical part 87 is the connection part between the output shaft 31 and the input shaft 25. is rotatably supported by a bearing 89.
ロータ91の中空軸93はヨーク83の内側円筒部87
に套装されている。内側円筒部87と中空軸93の対向
面には螺線溝が形成され、この螺線溝に沿って多数の鋼
球95が配列されている。The hollow shaft 93 of the rotor 91 is connected to the inner cylindrical portion 87 of the yoke 83.
is cloaked in. A spiral groove is formed on the opposing surfaces of the inner cylindrical portion 87 and the hollow shaft 93, and a large number of steel balls 95 are arranged along this spiral groove.
この螺線溝の両端には鋼球95の脱落防止用ストッパー
が設けられている。このようにして変換機構であるボー
ルねじ67が構成されている。中空軸93の左端には押
圧リング97が固定され、ニードルベアリング99を介
してクラッチ部63の押圧板79に当接している。Stoppers for preventing the steel ball 95 from falling off are provided at both ends of this spiral groove. In this way, the ball screw 67, which is a conversion mechanism, is constructed. A pressure ring 97 is fixed to the left end of the hollow shaft 93 and is in contact with a pressure plate 79 of the clutch portion 63 via a needle bearing 99.
モータ65は、路面状況などに応じて運転席から手動操
作されるか、又は例えば各車輪17,19.21.23
のスリップセンサからの信号に基づいて自動操作される
。The motor 65 may be operated manually from the driver's seat depending on the road surface conditions, or may be operated by each wheel 17, 19, 21, 23, for example.
Automatically operated based on signals from the slip sensor.
次にこのように構成された多板クラッチ61の機能を説
明すると、
モータ65に通電しロータ91を回転させると、ロータ
91はボールねじ67の方向変換機能によって左方へ前
進し、押圧リング97は回転しながらニードルベアリン
グ99を介してクラッチ部63を押圧しこれを締結させ
る。クラッチ部63が締結するとデファレンシャル装置
59において出力軸31とプーリ37とが連結されるの
でこれらの間の差動回転が停止又は制限される。モータ
65のトルクは電流値に比例するから電流値を変化させ
れば、クラッチ部63の締結力を任意の大きさに調節で
きる。クラッチ部63を解放するにはモータ65を逆方
向に回転させロータ91を右方へ後退させる。このよう
に、多板クラッチ61はデファレンシャル装置59の差
動制限装置として機能する。Next, the function of the multi-disc clutch 61 configured as described above will be explained. When the motor 65 is energized and the rotor 91 is rotated, the rotor 91 advances to the left by the direction changing function of the ball screw 67, and the press ring 97 While rotating, the clutch portion 63 is pressed through the needle bearing 99 to engage the clutch portion 63. When the clutch portion 63 is engaged, the output shaft 31 and the pulley 37 are connected in the differential device 59, so differential rotation therebetween is stopped or restricted. Since the torque of the motor 65 is proportional to the current value, the engagement force of the clutch portion 63 can be adjusted to an arbitrary magnitude by changing the current value. To release the clutch portion 63, the motor 65 is rotated in the opposite direction to move the rotor 91 backward to the right. In this way, the multi-plate clutch 61 functions as a differential limiting device for the differential device 59.
さらにこの機能を車両の性能に即して説明すると、良路
においては、手動又はセンサ検知による自動操作によっ
てクラッチ部63を解放すればデファレンシャル装置5
9が通常のセンターデフとして機能し路面条件に応じて
駆動力を前輪17゜19と後輪21.23に配分し走行
安定性を高める。又コーナリングに際しては前後輪間の
最適なグリップバランスが得られ操縦安定性が増す。又
、車庫入れのような低速急旋回の際にプロペラシャフト
11に生じるねじりをセンターデフ59が吸収するから
タイトコーナーブレーキング坦象は発生しない。Furthermore, to explain this function in accordance with the performance of the vehicle, on a good road, if the clutch part 63 is released manually or automatically by sensor detection, the differential device 5
9 functions as a normal center differential and distributes the driving force between the front wheels 17 degrees 19 and the rear wheels 21 degrees 23 depending on road conditions, improving driving stability. Also, when cornering, an optimal grip balance between the front and rear wheels can be obtained, increasing steering stability. Further, since the center differential 59 absorbs the twisting that occurs in the propeller shaft 11 when making a low-speed sharp turn such as when parking the vehicle, tight corner braking does not occur.
悪路において、例えば前輪17.19又は後輪21.2
3のいずれか一方がスリップしスタック状態に陥ったと
きはクラッチ部63を締結しセンターデフ59をロック
すれば他方の車輪にも駆動力が送られスタック状態から
脱出できる。On rough roads, e.g. front wheels 17.19 or rear wheels 21.2
If one of the wheels 3 slips and becomes stuck, the clutch 63 is engaged and the center differential 59 is locked, and driving force is sent to the other wheel, allowing the vehicle to escape from the stuck state.
この構成によれば、摩擦板73.75に電磁りラッチの
ように磁束を通さないから、ライニングを施した摩擦特
性の優れた摩擦板を自由に選択できる。従って、摩擦係
数μの大きい摩擦板を用いてクラッチ部63の最大締結
力(容量)を大ぎく設計することができる。又ライニン
グを施した摩擦板を用いたことにより、温度上昇に伴っ
て締結力が低下する、ブレーキのフェード現象に相当す
る、現象が起らない。又、作動時に鳴き音や振動音のよ
うな異常音が発生しない。その上電磁クラッチのような
ヒステリシス現象がないから解放時間が短く、空転トル
クが小さい。又、油圧式クラッチより部品点数が少なく
、配管も不要であり低コストである。According to this configuration, unlike an electromagnetic latch, magnetic flux does not pass through the friction plates 73, 75, so that a friction plate with excellent friction characteristics that is lined can be freely selected. Therefore, the maximum engagement force (capacity) of the clutch portion 63 can be designed to be large by using a friction plate having a large friction coefficient μ. Furthermore, by using a friction plate with a lining, a phenomenon corresponding to a brake fade phenomenon in which the fastening force decreases as the temperature rises does not occur. Furthermore, no abnormal noise such as squealing or vibration is generated during operation. Furthermore, since there is no hysteresis phenomenon as with electromagnetic clutches, the release time is short and the idle torque is small. In addition, it has fewer parts than a hydraulic clutch, does not require piping, and is low cost.
なお、クラッチ部63の作動時においてロータ91の回
転は数分の1回転以下であるから、変換機構としてはボ
ールねじ67の他に、カム機構をリターンスプリングと
併用して用いることができる。Note that since the rotation of the rotor 91 is less than a fraction of a rotation when the clutch portion 63 is operated, a cam mechanism can be used in combination with a return spring in addition to the ball screw 67 as the conversion mechanism.
この発明の多板クラッチ61は、差動制限装置として用
いる場合、上記の実施例のような遊星歯車タイプのデフ
ばかりでなく、他の型式のデフに用いることもできる。When the multi-plate clutch 61 of the present invention is used as a differential limiting device, it can be used not only for the planetary gear type differential as in the above embodiment, but also for other types of differentials.
又、前輪側や後輪側のデフに用いることもでき、また、
4輪駆動車の2WD−4WD切換機構として用いること
もできる。さらに、車両用に限らず産業全般において電
磁クラッチや油圧式クラッチと同じ用途に供することが
できることはいうまでもない。It can also be used for front and rear wheel differentials, and
It can also be used as a 2WD-4WD switching mechanism for a four-wheel drive vehicle. Furthermore, it goes without saying that it can be used for the same purposes as electromagnetic clutches and hydraulic clutches, not only for vehicles but in general industry.
[発明の効果]
このように、この発明の多板クラッチは種々の摩擦板を
用いることができ、異常音の発生を抑制できる。[Effects of the Invention] As described above, the multi-plate clutch of the present invention can use various friction plates, and can suppress the generation of abnormal noise.
第1図は一実施例をデファレンシャル装置とともに示す
断面図、第2図は第1図の実施例およびデファレンシャ
ル装置を用いた車両の駆動伝達系の概略図、第3図は摩
擦板の摩擦特性を示すグラフである。
59・・・デファレンシャル装置
61・・・多板クラッチ
63・・・クラッチ部
65・・・モータ
67・・・ボールねじ(変換機構)
6つ・・・ケース
71・・・ハブ部拐
73.75・・・摩擦板
代理人 弁理士 三 好 保 男
\
41 37 51 −州と
55L厘
3953′I
0 f
1′″Jll l+==jFig. 1 is a sectional view showing one embodiment together with a differential device, Fig. 2 is a schematic diagram of a drive transmission system of a vehicle using the embodiment shown in Fig. 1 and a differential device, and Fig. 3 shows the friction characteristics of the friction plate. This is a graph showing. 59...Differential device 61...Multi-plate clutch 63...Clutch section 65...Motor 67...Ball screw (conversion mechanism) 6...Case 71...Hub part removal 73.75 ...Friction plate agent Patent attorney Yasuo Miyoshi\41 37 51 -State and 55L 3953'I 0 f 1'''Jll l+==j
Claims (1)
内装されたハブ部材と、このハブ部材の外周と前記ケー
スの内周に各別に回転方向に係合し交互に配置された複
数枚の摩擦板とからなるクラッチ部と、外部制御可能な
モータと、このモータの回転力を変換して前記クラッチ
を押圧し締結させる変換機構とを備えたことを特徴とす
る多板クラッチ。A cylindrical case, a hub member housed in the case so as to be able to rotate relative to each other on the same axis, and a plurality of pieces that engage with each other in the rotational direction and are arranged alternately on the outer periphery of the hub member and the inner periphery of the case. What is claimed is: 1. A multi-disc clutch comprising: a clutch portion comprising a friction plate; an externally controllable motor; and a conversion mechanism that converts the rotational force of the motor to press and engage the clutch.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63063673A JPH01238719A (en) | 1988-03-18 | 1988-03-18 | Multiple disc clutch |
DE3908478A DE3908478A1 (en) | 1988-03-18 | 1989-03-15 | Multi-disc clutch |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63063673A JPH01238719A (en) | 1988-03-18 | 1988-03-18 | Multiple disc clutch |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH01238719A true JPH01238719A (en) | 1989-09-22 |
Family
ID=13236111
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP63063673A Pending JPH01238719A (en) | 1988-03-18 | 1988-03-18 | Multiple disc clutch |
Country Status (2)
Country | Link |
---|---|
JP (1) | JPH01238719A (en) |
DE (1) | DE3908478A1 (en) |
Families Citing this family (27)
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---|---|---|---|---|
US5199325A (en) * | 1991-09-12 | 1993-04-06 | Dana Corporation | Electronic shift or clutch actuator for a vehicle transmission |
DE4140122C2 (en) * | 1991-12-05 | 1994-07-07 | Daimler Benz Ag | Arrangement for the electric motor actuation of a frictional connection between two gear members of a gear transmission of a motor vehicle |
US5934430A (en) * | 1997-06-19 | 1999-08-10 | Eaton Corporation | Electrically operated clutch |
US6780132B2 (en) * | 2002-08-02 | 2004-08-24 | Visteon Global Technologies, Inc. | Selectively actuated transfer case |
US6766889B1 (en) | 2003-02-11 | 2004-07-27 | New Venture Gear, Inc. | Wedge fork clutch actuator for driveline clutches |
DE10307018B4 (en) * | 2003-02-20 | 2016-01-07 | Zf Friedrichshafen Ag | Transfer case with adjustable clutch |
DE10307019B4 (en) | 2003-02-20 | 2015-12-03 | Zf Friedrichshafen Ag | Transfer case with adjustable clutch |
DE10307017B4 (en) * | 2003-02-20 | 2015-12-03 | Zf Friedrichshafen Ag | Transfer case with adjustable clutch |
US7175557B2 (en) | 2003-02-21 | 2007-02-13 | Magna Powertrain Usa, Inc. | Torque vectoring device having an electric motor/brake actuator and friction clutch |
US6808053B2 (en) | 2003-02-21 | 2004-10-26 | New Venture Gear, Inc. | Torque transfer device having an electric motor/brake actuator and friction clutch |
US7211019B2 (en) | 2003-02-21 | 2007-05-01 | Magna Powertrain Usa, Inc. | Torque vectoring drive mechanism having a power sharing control system |
US7175558B2 (en) | 2003-03-07 | 2007-02-13 | Magna Powertrain Usa, Inc. | Torque vectoring drive units with worm driven ball screw clutches |
US6808037B1 (en) | 2003-04-08 | 2004-10-26 | New Venture Gear, Inc. | On-demand transfer case |
US6905436B2 (en) | 2003-10-30 | 2005-06-14 | Magna Drivetrain Of America, Inc. | Two-speed transfer case with adaptive clutch control |
US7125364B2 (en) | 2003-11-07 | 2006-10-24 | Magna Powertrain Usa, Inc. | Control strategy for active torque control |
US6929577B2 (en) | 2003-11-24 | 2005-08-16 | Magna Drivetrain Of America, Inc. | Clutch actuation system for two-speed active transfer case |
US7399251B2 (en) | 2003-11-24 | 2008-07-15 | Magna Powertrain Usa, Inc. | Two-speed transfer case |
US7338403B2 (en) | 2004-08-30 | 2008-03-04 | Magna Powertrain Usa, Inc. | Torque coupling with power-operated clutch actuator |
DE102004053121B4 (en) * | 2004-11-03 | 2011-12-29 | Iglhaut Gmbh | Motor vehicle with four-wheel drive |
US7111716B2 (en) | 2005-01-26 | 2006-09-26 | Magna Powertrain Usa, Inc. | Power-operated clutch actuator for torque transfer mechanisms |
AT8636U1 (en) | 2005-04-28 | 2006-10-15 | Magna Drivetrain Ag & Co Kg | DISTRIBUTION GEARBOX FOR MOTOR VEHICLES WITH A CONTROLLED FRICTION COUPLING |
US7527133B2 (en) | 2005-07-28 | 2009-05-05 | Magna Powertrain Usa, Inc. | Power-operated clutch actuator for torque couplings |
US7540820B2 (en) | 2005-09-01 | 2009-06-02 | Magna Powertrain Usa, Inc. | Two-speed transfer case with ballramp clutch actuator |
US7650808B2 (en) | 2006-02-03 | 2010-01-26 | Magna Powertrain Usa, Inc. | Sprial cam clutch actuation system for two-speed transfer case |
US7694598B2 (en) | 2006-04-26 | 2010-04-13 | Magna Powertrain Ag & Co Kg | Two-speed transfer case with adaptive torque transfer clutch |
DE102006030033A1 (en) * | 2006-06-29 | 2008-01-03 | Zf Friedrichshafen Ag | Electric motor actuator for actuation of friction coupling and/or automated gear brake in motor vehicle, has rotor and circular actuating element movable axially to thread drive by streaming electric motor |
JPWO2022107267A1 (en) * | 2020-11-19 | 2022-05-27 |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE417194C (en) * | 1924-06-12 | 1925-08-08 | Magnet Werk G M B H Eisenach | Friction clutch operated by an electric motor |
DE513823C (en) * | 1929-12-21 | 1930-12-03 | Magnet Werk G M B H | Friction clutch operated by an electric motor |
US3483410A (en) * | 1967-11-21 | 1969-12-09 | Beckman Instruments Inc | High torque motor |
US3644763A (en) * | 1970-12-08 | 1972-02-22 | Allard Instr Corp | Limited angle dc torque motor |
-
1988
- 1988-03-18 JP JP63063673A patent/JPH01238719A/en active Pending
-
1989
- 1989-03-15 DE DE3908478A patent/DE3908478A1/en not_active Ceased
Also Published As
Publication number | Publication date |
---|---|
DE3908478A1 (en) | 1989-10-05 |
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