JP3005167B2 - Variable phase device - Google Patents
Variable phase deviceInfo
- Publication number
- JP3005167B2 JP3005167B2 JP6324874A JP32487494A JP3005167B2 JP 3005167 B2 JP3005167 B2 JP 3005167B2 JP 6324874 A JP6324874 A JP 6324874A JP 32487494 A JP32487494 A JP 32487494A JP 3005167 B2 JP3005167 B2 JP 3005167B2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- planetary gear
- rotation
- transmission
- shaft
- 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.)
- Expired - Fee Related
Links
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- Structure Of Transmissions (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は可変位相装置に関し、詳
しくは、一方側の回転軸と他方側の回転軸との間に差動
機構を介装し、この差動機構を差動機能停止させた伝動
状態として前記の両回転軸を互いに等しい角速度で連動
回転させる軸関係保持操作と、前記差動機構を差動機能
させて前記の両回転軸を互いに異なる角速度で所要角度
だけ相対回転動作させる軸関係変更操作とを行う軸関係
操作手段を設けた可変位相装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable phase shifter, and more particularly to a variable phase shifter, in which a differential mechanism is interposed between a rotary shaft on one side and a rotary shaft on the other side, and the differential mechanism is stopped. An axial relationship maintaining operation of interlocking rotation of the two rotating shafts at the same angular velocity as the transmitted power state, and a relative rotation operation of the two rotating shafts at different angular velocities by a required angle by causing the differential mechanism to perform a differential function. The present invention relates to a variable phase device provided with an axis relation operation means for performing an axis relation change operation to be performed.
【０００２】[0002]
【従来の技術】上記の可変位相装置（図６参照）は、軸
関係保持操作により差動機構１５を差動機能停止させた
伝動状態として両回転軸１３ｍ，１３ｎを互いに等しい
角速度で連動回転させることにより、これら回転軸１３
ｍ，１３ｎの回転位相関係を一定に保つ回転伝動状態を
現出し、また、軸関係変更操作により差動機構１５を差
動機能させて両回転軸１３ｍ，１３ｎを互いに異なる角
速度で所要角度だけ相対回転動作させることにより、こ
れら回転軸１３ｍ，１３ｎの回転位相関係を所要角度だ
け変更するものである。2. Description of the Related Art The above-mentioned variable phase device (see FIG. 6) rotates both rotating shafts 13m and 13n at the same angular velocity in a transmission state in which the differential mechanism 15 is stopped by a shaft relation maintaining operation. Therefore, these rotating shafts 13
A rotational transmission state in which the rotational phase relationship between m and 13n is kept constant, and the differential mechanism 15 is made to function differentially by changing the axial relationship, so that the two rotational shafts 13m and 13n are relatively rotated at different angular velocities by a required angle. By rotating, the rotational phase relationship between the rotating shafts 13m and 13n is changed by a required angle.
【０００３】すなわち、この軸関係変更操作の後、上記
の軸関係保持操作を行うことにより、両回転軸１３ｍ，
１３ｎを変更後の新たな回転位相関係に保って連動回転
させるものであり、このように回転伝動における両回転
軸の回転位相関係を適宜に変更できるようにすること
で、回転伝動を用いる各種機器の運転状態の変更を可能
にする。[0003] That is, after the axial relationship changing operation, the above-mentioned axial relationship maintaining operation is performed, whereby both rotating shafts 13m, 13m,
13n is rotated in an interlocked manner while maintaining the new rotational phase relationship after the change, and by enabling the rotational phase relationship between the two rotating shafts in the rotational transmission to be appropriately changed, various devices using the rotational transmission It is possible to change the operation state of the vehicle.
【０００４】なお、図６に示す従来装置では、差動機構
１５として、一方側の回転軸１３ｍとともに回転する第
１ギア１６と、他方側の回転軸１３ｎとともに回転する
第２ギア１７と、位置固定された状態で第１ギア１６に
対し咬合する第１遊星ギア１６ａと、第２ギア１７に対
し咬合する第２遊星ギア１７ａと、第２ギア１７の周り
での第２遊星ギア１７ａの位置変更にかかわらず第１遊
星ギア１６ａ及び第２遊星ギア１７ａの両方に対して咬
合する中間ギア１８とを備える遊星ギア式差動機構を採
用している。[0006] In the conventional device shown in FIG. 6, as a differential mechanism 15, a first gear 16 rotating with a rotating shaft 13m on one side, a second gear 17 rotating with a rotating shaft 13n on the other side, A first planetary gear 16a engaging with the first gear 16 in a fixed state, a second planetary gear 17a engaging with the second gear 17, and a position of the second planetary gear 17a around the second gear 17 Regardless of the change, a planetary gear differential mechanism including an intermediate gear 18 that meshes with both the first planetary gear 16a and the second planetary gear 17a is employed.
【０００５】また、上記の軸関係保持操作と軸関係変更
操作を行う軸関係操作手段には、第２遊星ギア１７ａを
支持する可動キャリア１９を介して、第２遊星ギア１７
ａの位置を第２ギア１７の周りで変更する操作と、その
変更位置に固定する操作とを行うギア式操作機構２０を
採用している。[0005] The second planetary gear 17 is provided to a shaft-related operation means for performing the above-mentioned shaft-relation holding operation and shaft-relation changing operation via a movable carrier 19 supporting a second planetary gear 17a.
A gear-type operation mechanism 20 that performs an operation of changing the position a around the second gear 17 and an operation of fixing the position at the changed position is adopted.
【０００６】つまり、軸関係保持操作としては、第２遊
星ギア１７ａの位置を第２ギア１７の周りで固定するこ
とにより、遊星ギア式差動機構１５において差動を伴わ
ない状態で第１ギア１６、第１遊星ギア１６ａ、中間ギ
ア１８、第２遊星ギア１７ａ、第２ギア１７にわたり回
転伝動させ、これにより、予め選定したギア比条件のも
とで、両回転軸１３ｍ，１３ｎを互いに等しい角速度で
連動回転させる。In other words, as the axial relationship maintaining operation, the position of the second planetary gear 17a is fixed around the second gear 17, so that the planetary gear type differential mechanism 15 can operate the first gear 17 without any differential. 16, the first planetary gear 16a, the intermediate gear 18, the second planetary gear 17a, and the second gear 17 are rotationally transmitted, so that the two rotating shafts 13m and 13n are equal to each other under a predetermined gear ratio condition. Rotate in conjunction with angular velocity.
【０００７】また、軸関係変更操作としては、第２遊星
ギア１７ａの位置を第２ギア１７の周りで変更すること
により、この位置変更過程で第１ギア１６、第１遊星ギ
ア１６ａ、中間ギア１８、第２遊星ギア１７ａ、第２ギ
ア１７にわたる回転伝動に差動を生じさせ、これによ
り、第２ギア１７の周りでの第２遊星ギア１７ａの位置
変更角度に対応する角度だけ、両回転軸１３ｍ，１３ｎ
を互いに異なる角速度で相対回転動作させる。In the axial relationship changing operation, the position of the second planetary gear 17a is changed around the second gear 17, so that the first gear 16, the first planetary gear 16a, the intermediate gear 18, causing a differential in the rotational transmission across the second planetary gear 17a and the second gear 17, thereby allowing the two rotations by an angle corresponding to the position change angle of the second planetary gear 17a around the second gear 17. Shaft 13m, 13n
Are rotated relative to each other at different angular velocities.
【０００８】そして、従来、この種の可変位相装置で
は、軸関係保持状態において両回転軸１３ｍ，１３ｎに
わたり回転伝動させるのに、上記の如く、差動機構１５
の構成ギア（すなわち、上記例では第１ギア１６、第１
遊星ギア１６ａ、中間ギア１８、第２遊星ギア１７ａ、
第２ギア１７）のみをもって回転力伝達を行う構成とし
ていた。Conventionally, in this type of variable phase device, when the rotation is transmitted over both the rotating shafts 13m and 13n in the state of maintaining the axial relationship, as described above, the differential mechanism 15 is used.
(That is, the first gear 16 and the first gear 16 in the above example)
A planetary gear 16a, an intermediate gear 18, a second planetary gear 17a,
The configuration is such that the rotational force is transmitted only by the second gear 17).
【０００９】[0009]
【発明が解決しようとする課題】しかし、従来装置にお
いては、両回転軸１３ｍ，１３ｎにわたる回転伝動にお
いて回転トルクが全て差動機構１５の構成ギアに作用す
るため、また特に、トルク変動が有る場合において、そ
のピークトルクが全て差動機構１５の構成ギアに作用す
るため、差動機構１５の早期のギア摩損や破損を生じ易
く、耐久性の面で問題があり、また、高耐久性を確保す
るには構成ギアの全てを強大にすることが必要となって
装置コストが高くなる問題があった。However, in the conventional apparatus, since all the rotational torque acts on the constituent gears of the differential mechanism 15 in the rotation transmission across both the rotating shafts 13m and 13n, and especially when there is a torque fluctuation. In this case, all of the peak torque acts on the constituent gears of the differential mechanism 15, so that the differential mechanism 15 is liable to cause early gear wear and breakage, and there is a problem in durability, and high durability is ensured. In this case, it is necessary to make all of the constituent gears large, and there is a problem that the cost of the apparatus is increased.
【００１０】以上の実情に対し、本発明は、装置耐久性
の向上を基本目的とし、また、操作構成の簡略化、及
び、操作の簡便化を付加目的とする。[0010] In view of the above circumstances, the present invention has a basic object of improving the durability of the apparatus, and has an additional object of simplifying the operation configuration and simplifying the operation.
【００１１】[0011]
〔第１特徴構成〕請求項１に係る、本発明の第１特徴構
成は、一方側の回転軸と他方側の回転軸との間に差動機
構を介装し、この差動機構を差動機能停止させた伝動状
態として前記の両回転軸を互いに等しい角速度で連動回
転させる軸関係保持操作と、前記差動機構を差動機能さ
せて前記の両回転軸を互いに異なる角速度で所要角度だ
け相対回転動作させる軸関係変更操作とを行う軸関係操
作手段を設けた構成において、前記の軸関係保持操作に
おいて伝動作用状態とし、かつ、前記の軸関係変更操作
において伝動遮断状態とするクラッチ機構を、前記差動
機構とは並列の関係で前記両回転軸の間に介装したこと
にある。[First characteristic configuration] According to a first characteristic configuration of the present invention, a differential mechanism is interposed between a rotation shaft on one side and a rotation shaft on the other side. A shaft relation maintaining operation of interlockingly rotating the two rotating shafts at the same angular velocity as the transmission state in which the moving function is stopped, and causing the differential mechanism to perform a differential function so that the two rotating shafts are rotated at different angular velocities by a required angle. In a configuration provided with an axis relation operation means for performing an axis relation change operation for performing a relative rotation operation, a clutch mechanism that is in a transmission operation state in the axis relation holding operation, and is in a transmission cutoff state in the axis relation change operation. And the differential mechanism is interposed between the two rotating shafts in a parallel relationship.
【００１２】〔第２特徴構成〕請求項２に係る、本発明
の第２特徴構成は、上記の第１特徴構成の実施において
好適な具体構成を特定するものであり、前記差動機構
は、前記の一方側回転軸とともに回転する第１ギアと、
前記の他方側回転軸とともに回転する第２ギアと、位置
固定された状態で前記第１ギアに対し咬合する第１遊星
ギアと、前記第２ギアに対し咬合する第２遊星ギアと、
前記第２ギアの周りでの前記第２遊星ギアの位置変更に
かかわらず前記第１遊星ギア及び前記第２遊星ギアの両
方に対して咬合する中間ギアとを備える遊星ギア式に構
成し、前記の軸関係操作手段は、前記の軸関係保持操作
として前記第２遊星ギアの位置を前記第２ギアの周りで
固定する操作と、前記の軸関係変更操作として前記第２
遊星ギアの位置を前記第２ギアの周りで変更する操作と
を行う構成としてあることにある。[Second feature configuration] A second feature configuration of the present invention according to claim 2 specifies a preferred specific configuration in the implementation of the first feature configuration, and the differential mechanism includes: A first gear that rotates together with the one-side rotating shaft;
A second gear that rotates together with the other rotation shaft, a first planetary gear that meshes with the first gear in a fixed state, and a second planetary gear that meshes with the second gear,
A planetary gear type including an intermediate gear that meshes with both the first planetary gear and the second planetary gear regardless of a change in the position of the second planetary gear around the second gear; The axial relationship operating means includes: an operation for fixing the position of the second planetary gear around the second gear as the axial relationship maintaining operation; and the second axial relationship as the axial relationship changing operation.
The operation of changing the position of the planetary gear around the second gear is performed.
【００１３】〔第３特徴構成〕請求項３に係る、本発明
の第３特徴構成は、前記の第１又は第２特徴構成の実施
において好適な具体構成を特定するものであり、前記ク
ラッチ機構として、回転に伴い自動的に伝動作用状態に
切り換わり、かつ、回転停止に伴い自動的に伝動遮断状
態に切り換わる自動クラッチ機構を採用したことにあ
る。[Third feature configuration] A third feature configuration of the present invention according to claim 3 is to specify a specific configuration suitable for implementing the first or second feature configuration, and the clutch mechanism is provided. An automatic clutch mechanism that automatically switches to a transmission operation state with rotation and automatically switches to a transmission cutoff state with rotation stop is adopted.
【００１４】〔第４特徴構成〕請求項４に係る、本発明
の第４特徴構成は、上記の第１又は第２特徴構成の実施
において好適な具体構成を特定するものであり、前記の
軸関係操作手段と前記クラッチ機構とを連係動作させる
連係操作手段を設けたことにある。[Fourth feature configuration] A fourth feature configuration of the present invention according to claim 4 is to specify a preferred specific configuration in the implementation of the first or second feature configuration, and the shaft There is provided a link operation means for linking the related operation means and the clutch mechanism.
【００１５】[0015]
〔第１特徴構成の作用〕第１特徴構成では（図２及び図
３参照）、軸関係保持操作において、すなわち、差動機
構１５を差動機能停止させた伝動状態として両回転軸１
３ｍ，１３ｎを互いに等しい角速度で連動回転させる状
態において、クラッチ機構２１を伝動作用状態とするこ
とにより、差動機構１５とは並列の関係のクラッチ機構
２１を介しての両回転軸１３ｍ，１３ｎにわたる回転伝
動を行わせ、これにより、両回転軸１３ｍ，１３ｎにわ
たる回転伝動上で差動機構１５の構成ギア１６，１６
ａ，１８，１７ａ，１７に作用する回転トルクを軽減す
る。[Operation of the first characteristic configuration] In the first characteristic configuration (see FIGS. 2 and 3), in the axial relationship maintaining operation, that is, in the transmission state in which the differential mechanism 15 has stopped the differential function, the two rotary shafts 1
When the clutch mechanism 21 is set to the transmission operation state in a state where the 3m and 13n are interlockedly rotated at the same angular velocity, the clutch mechanism 21 extends over both rotation shafts 13m and 13n via the clutch mechanism 21 in a parallel relationship with the differential mechanism 15. Rotational transmission is performed, whereby the constituent gears 16, 16 of the differential mechanism 15 are rotated on the rotational transmission over both rotation shafts 13m, 13n.
a, 18, 17a, and 17 The rotational torque acting on 17 is reduced.
【００１６】また、軸関係変更操作において、すなわ
ち、差動機構１５を差動機能させて両回転軸１３ｍ，１
３ｎを互いに異なる角速度で所要角度だけ相対回転動作
させる状態においては、上記のクラッチ機構２１を伝動
遮断状態とすることにより、両回転軸１３ｍ，１３ｎの
互いに異なる角速度での相対回転動作を許容する。In the operation of changing the axial relationship, that is, by making the differential mechanism 15 perform the differential function, the two rotary shafts 13m, 1
In a state in which the clutch 3n is rotated relative to the required angle at different angular velocities, the clutch mechanism 21 is set in the transmission cutoff state, thereby permitting relative rotation between the two rotating shafts 13m and 13n at different angular velocities.
【００１７】なお、両回転軸１３ｍ，１３ｎの互いに異
なる角速度での相対回転動作とは、両回転軸１３ｍ，１
３ｎのうちの一方を回転停止させた状態で他方を回転動
作させる形態の相対回転動作を含む。The relative rotation operation of the two rotating shafts 13m and 13n at different angular velocities means that the two rotating shafts 13m and 13n
3n includes a relative rotation operation in which one of the rotations is stopped while the other is stopped.
【００１８】〔第２特徴構成の作用〕第２特徴構成では
（同図２及び図３参照）、軸関係操作手段２０による軸
関係保持操作として、第２遊星ギア１７ａの位置を第２
ギア１７の周りで固定することにより、遊星ギア式差動
機構１５において差動を伴わない状態で第１ギア１６、
第１遊星ギア１６ａ、中間ギア１８、第２遊星ギア１７
ａ、第２ギア１７にわたり回転伝動させ、これにより、
予め選定したギア比条件のもとで、両回転軸１３ｍ，１
３ｎを互いに等しい角速度で両回転軸１３ｍ，１３ｎの
回転位相関係を保って連動回転させる。[Operation of Second Characteristic Configuration] In the second characteristic configuration (see FIGS. 2 and 3), the position of the second planetary gear 17a is set to the second position as the axial relationship maintaining operation by the axial relationship operating means 20.
By fixing around the gear 17, the first gear 16,
First planetary gear 16a, intermediate gear 18, second planetary gear 17
a, rotationally transmitted through the second gear 17, whereby
Under the gear ratio condition selected in advance, both rotating shafts 13m, 1
3n are rotated at the same angular velocity while maintaining the rotational phase relationship between the two rotating shafts 13m and 13n.
【００１９】また、軸関係操作手段２０による軸関係変
更操作として、第２遊星ギア１７ａの位置を第２ギア１
７の周りで変更することにより、この位置変更過程で第
１ギア１６、第１遊星ギア１６ａ、中間ギア１８、第２
遊星ギア１７ａ、第２ギア１７にわたる回転伝動に差動
を生じさせて、第２ギア１７の周りでの第２遊星ギア１
７ａの位置変更角度に対応する角度だけ、両回転軸１３
ｍ，１３ｎを互いに異なる角速度で相対回転動作させ、
これにより、両回転軸１３ｍ，１３ｎの回転位相関係を
変更する。As the axial relationship changing operation by the axial relationship operating means 20, the position of the second planetary gear 17a is changed to the second gear 1
7, the first gear 16, the first planetary gear 16a, the intermediate gear 18, the second gear
By causing a differential in the rotation transmission across the planetary gear 17a and the second gear 17, the second planetary gear 1 around the second gear 17
7a, the two rotation shafts 13 are shifted by an angle corresponding to the position change angle.
m and 13n are relatively rotated at different angular velocities,
This changes the rotational phase relationship between the two rotating shafts 13m and 13n.
【００２０】そして、軸関係保持操作としての第２遊星
ギア１７ａの位置固定時には、遊星ギア式差動機構１５
と並列の関係の前記クラッチ機構２１を伝動作用状態に
して、このクラッチ機構２１を介しての回転伝動を行わ
せることにより、遊星ギア式差動機構１５の構成ギア
（第１ギア１６，第１遊星ギア１６ａ，中間ギア１８，
第２遊星ギア１７ａ，第２ギア１７）に作用する回転ト
ルクを軽減し、また、軸関係変更操作としての第２遊星
ギア１７ａの位置変更時には、上記のクラッチ機構２１
を伝動遮断状態とすることで、両回転軸１３ｍ，１３ｎ
の互いに異なる角速度での相対回転動作を許容する。When the position of the second planetary gear 17a is fixed as the operation for maintaining the axial relationship, the planetary gear differential mechanism 15
By setting the clutch mechanism 21 in a parallel relationship with the transmission mechanism in a transmission operation state and performing rotation transmission via the clutch mechanism 21, the constituent gears of the planetary gear type differential mechanism 15 (the first gear 16, the first gear 16, Planetary gear 16a, intermediate gear 18,
The rotational torque acting on the second planetary gears 17a and the second gear 17) is reduced, and when the position of the second planetary gear 17a is changed as the axial relation changing operation, the clutch mechanism 21 is used.
Is set to the transmission cutoff state, so that both rotating shafts 13m, 13n
Are allowed to rotate at different angular velocities.
【００２１】〔第３特徴構成の作用〕第３特徴構成では
（同図２及び図３参照）、回転運転を停止して両回転軸
１３ｍ，１３ｎの連動回転を停止することにより、この
回転停止に伴い自動クラッチ機構２１を伝動作用状態か
ら伝動遮断状態に自動的に切り換わり動作させて、両回
転軸１３ｍ，１３ｎの互いに異なる角速度での相対回転
動作を許す状態とし、この状態で、前記の軸関係変更操
作を行うことにより、両回転軸１３ｍ，１３ｎの相対回
転動作として、両回転軸１３ｍ，１３ｎのうちの一方は
回転停止させた状態で差動機構１５を差動機能させて他
方を回転動作させ、これにより、両回転軸１３ｍ，１３
ｎの回転位相関係を変更する。[Operation of the Third Characteristic Configuration] In the third characteristic configuration (see FIGS. 2 and 3), the rotation operation is stopped to stop the rotation of both rotating shafts 13m and 13n, thereby stopping the rotation. As a result, the automatic clutch mechanism 21 is automatically switched from the transmission operation state to the transmission cutoff state to operate, thereby allowing the relative rotation of the two rotating shafts 13m and 13n at mutually different angular velocities. By performing the axial relationship changing operation, as a relative rotation operation between the two rotating shafts 13m and 13n, one of the two rotating shafts 13m and 13n is caused to have the differential mechanism 15 perform the differential function while the other is stopped, and the other is rotated. The rotary operation is performed.
Change the rotational phase relationship of n.
【００２２】また、軸関係保持操作を行った状態で回転
運転を再開することにより、差動機能停止させた状態で
の差動機構１５の伝動作用により両回転軸１３ｍ，１３
ｎを連動回転させるようにしながら、この回転開始に伴
い自動クラッチ機構２１を伝動遮断状態から伝動作用状
態に自動的に切り換わり動作させ、これにより、クラッ
チ機構２１を介しての回転伝動状態で、両回転軸１３
ｍ，１３ｎを互いに等しい角速度で両回転軸１３ｍ，１
３ｎの回転位相関係を保って連動回転させる。Further, by restarting the rotation operation in a state where the shaft relation maintaining operation is performed, the two rotation shafts 13m and 13m are used for the transmission operation of the differential mechanism 15 in a state where the differential function is stopped.
n, the automatic clutch mechanism 21 is automatically switched from the transmission cut-off state to the transmission operation state in accordance with the start of the rotation, and is operated. Both rotating shafts 13
m, 13n at the same angular velocity to both rotating shafts 13m, 1
The interlocking rotation is performed while maintaining the rotation phase relationship of 3n.
【００２３】〔第４特徴構成の作用〕第４特徴構成では
（図５参照）、連係操作手段２２の連係機能により軸関
係操作手段２０とクラッチ機構２１とを連係動作させる
ことで、軸関係保持操作においてはクラッチ機構２１を
伝動作用状態にし、また、軸関係変更操作においてクラ
ッチ機構２１を伝動遮断状態にする。[Operation of Fourth Characteristic Configuration] In the fourth characteristic configuration (see FIG. 5), the axial relation maintaining means 20 and the clutch mechanism 21 are operated in cooperation by the cooperation function of the cooperation operation means 22, thereby maintaining the axial relation. In operation, the clutch mechanism 21 is set to the transmission operation state, and in the shaft relation changing operation, the clutch mechanism 21 is set to the transmission cutoff state.
【００２４】[0024]
〔第１特徴構成の効果〕本発明の第１特徴構成によれ
ば、差動機構の構成ギアに作用する回転トルクを軽減で
きることで、差動機構の早期のギア摩損や破損を防止し
て装置の耐久性・信頼性を高めることができ、また、差
動機構の必要強度を低減できることで装置コストの低減
も可能となる。[Effects of the first characteristic configuration] According to the first characteristic configuration of the present invention, the rotational torque acting on the constituent gears of the differential mechanism can be reduced, thereby preventing early gear wear and breakage of the differential mechanism. The durability and reliability of the differential mechanism can be improved, and the required strength of the differential mechanism can be reduced, so that the cost of the apparatus can be reduced.
【００２５】〔第２特徴構成の効果〕本発明の第２特徴
構成によれば、遊星ギア式差動機構を採用する構成にお
いて上記第１特徴構成の効果を得ることができる。[Effect of the second characteristic configuration] According to the second characteristic configuration of the present invention, the effect of the first characteristic configuration can be obtained in a configuration employing a planetary gear differential mechanism.
【００２６】また、第１ギア、第１遊星ギア、中間ギ
ア、第２遊星ギア、第２ギアを構成ギアとする前記の遊
星ギア式差動機構においては、互いに同方向に回転する
第１ギアと第２ギアとの間にクラッチ機構を配備する形
態で、クラッチ機構を両回転軸間に介装でき、これによ
り、差動機構の外側に両回転軸にわたる迂回伝動系を設
けて、この迂回伝動系にクラッチ機構を介装する形態に
比べ、装置構成をコンパクト化し得る。Further, in the above-mentioned planetary gear type differential mechanism having the first gear, the first planetary gear, the intermediate gear, the second planetary gear, and the second gear as constituent gears, the first gear rotating in the same direction as each other. The clutch mechanism can be interposed between the two rotation shafts in a form in which a clutch mechanism is provided between the first gear and the second gear. With this configuration, a bypass transmission system extending over both the rotation shafts is provided outside the differential mechanism. The device configuration can be made more compact than in a configuration in which a clutch mechanism is interposed in the transmission system.
【００２７】〔第３特徴構成の効果〕本発明の第３特徴
構成によれば、回転運転を停止させた状態で軸関係変更
操作を行うことにおいて、回転停止に伴いクラッチ機構
が自動的に伝動遮断状態に切り換わり動作し、また、軸
関係保持操作を行った状態で回転運転を再開することに
おいて、回転開始に伴いクラッチ機構が自動的に伝動作
用状態に切り換わり動作するから、クラッチ機構を外部
から切り換え操作する専用の切り換え操作機構が不要で
あり、これにより、装置構成を簡略化し得る。[Effects of the third characteristic configuration] According to the third characteristic configuration of the present invention, when the shaft relation changing operation is performed while the rotation operation is stopped, the clutch mechanism is automatically transmitted with the rotation stop. When the clutch mechanism is automatically switched to the transmission operation state at the start of rotation, the clutch mechanism is automatically switched to the transmission operation state. There is no need for a dedicated switching operation mechanism for performing an external switching operation, so that the device configuration can be simplified.
【００２８】また、回転運転の停止時を利用して回転位
相関係の変更を行う場合には、実質的に軸関係操作手段
による操作のみで簡便に回転位相関係の変更を行うこと
ができる。Further, when the rotation phase relationship is changed by using the time when the rotation operation is stopped, the rotation phase relationship can be easily and simply changed only by the operation of the axial relationship operation means.
【００２９】〔第４特徴構成の効果〕本発明の第４特徴
構成によれば、軸関係操作手段との連係動作でクラッチ
機構が切り換わることにより、軸関係操作手段による操
作とクラッチ機構の切り換え操作とを各別に行う形態に
比べ、操作が簡便になる。[Effect of Fourth Characteristic Configuration] According to the fourth characteristic configuration of the present invention, the clutch mechanism is switched by the cooperative operation with the shaft-related operation means, whereby the operation by the shaft-related operation means and the switching of the clutch mechanism are performed. The operation is simpler than in the case where the operation is performed separately.
【００３０】[0030]
【実施例】図１は、スターリングサイクル機器の一例と
してのエンジン駆動式の冷凍機ないしヒートポンプを示
し、１はエンジン、２はエンジン１により駆動される熱
機器部であり、エンジン１において、３はエンジン出力
軸、４は燃料路、５は吸気路、６はエンジン排ガスＥの
排気路、７はエンジン冷却水Ｗの循環路である。FIG. 1 shows an engine-driven refrigerator or heat pump as an example of a Stirling cycle device, wherein 1 is an engine, 2 is a heating device section driven by the engine 1, and 3 is the engine 1. An engine output shaft, 4 is a fuel path, 5 is an intake path, 6 is an exhaust path of engine exhaust gas E, and 7 is a circulation path of engine cooling water W.
【００３１】一方、熱機器部２において、８ａは低温シ
リンダ室、８ｂは中温シリンダ室、８ｃは高温シリンダ
室であり、これらシリンダ室８ａ，８ｂ，８ｃは、各々
に装備したピストン９ａ，９ｂ，９ｃの往復動作により
作動ガスＧ（例えばヘリウムガスや水素ガスなど）の吐
出と吸入を周期的に行う。On the other hand, in the thermal equipment section 2, reference numeral 8a denotes a low-temperature cylinder chamber, 8b denotes a medium-temperature cylinder chamber, and 8c denotes a high-temperature cylinder chamber. These cylinder chambers 8a, 8b, 8c are provided with pistons 9a, 9b, The discharge and suction of the working gas G (for example, helium gas, hydrogen gas, etc.) are periodically performed by the reciprocating operation of 9c.
【００３２】１０は各シリンダ室８ａ，８ｂ，８ｃを取
扱い温度の順に連通させるガス連通路であり、このガス
連通路１０において連通順位が隣合うシリンダ室間の夫
々には、蓄熱機能により一方のシリンダ室側と他方のシ
リンダ室側とを温度的に区分する再生熱交換器１１ｍ，
１１ｎを介装してある。Numeral 10 denotes a gas communication passage for connecting the cylinder chambers 8a, 8b, 8c in order of the handling temperature. In the gas communication passage 10, each of the adjacent cylinder chambers is connected to one of the adjacent cylinder chambers by a heat storage function. A regenerative heat exchanger 11m for dividing the cylinder chamber side and the other cylinder chamber side in temperature,
11n is interposed.
【００３３】また、１２ａは冷熱要求装置Ｘとの間で循
環させる冷熱媒Ｃに対して低温シリンダ室８ａを吸熱作
用させる低温吸熱器、１２ｂは温熱要求装置Ｙとの間で
循環させる温熱媒Ｈに対して中温シリンダ室８ｂを放熱
作用させる中温放熱器、１２ｃは排気路６により導かれ
るエンジン排ガスＥの保有熱を高温シリンダ室８ｃに付
与する高温加熱器である。Reference numeral 12a denotes a low-temperature heat absorber for absorbing the heat of the low-temperature cylinder chamber 8a with respect to the cooling medium C circulated between the cooling medium requesting apparatus X, and 12b denotes a heating medium H circulated to the heating request apparatus Y. A medium temperature radiator 12c for radiating the medium temperature cylinder chamber 8b, and a high temperature heater 12c for giving the retained heat of the engine exhaust gas E guided by the exhaust path 6 to the high temperature cylinder chamber 8c.
【００３４】なお、温熱要求装置Ｙに対しては、温熱媒
Ｈを介して中温シリンダ室８ｂの放出温熱を付与するこ
とに加え、冷却水循環路７を介して導く冷却作用後のエ
ンジン冷却水Ｗの保有温熱を付与する。It is to be noted that, in addition to the provision of the release heat of the medium-temperature cylinder chamber 8 b via the heating medium H to the heat requesting device Y, the engine cooling water W after the cooling action guided through the cooling water circulation path 7 is provided. The holding heat of is given.
【００３５】１３は各ピストン９ａ，９ｂ，９ｃを連動
動作させる回転伝動系としてエンジン出力軸３に連結し
た回転軸であり、この回転軸１３には、各シリンダ室８
ａ，８ｂ，８ｃの配置に合わせてエンジン出力軸３との
連結側から順に、低温シリンダ室８ａのピストン９ａを
連結する第１クランク１４ａ、中温シリンダ室８ｂのピ
ストン９ｂを連結する第２クランク１４ｂ、高温シリン
ダ室８ｃのピストン９ｃを連結する第３クランク１４ｃ
を設けてある。Reference numeral 13 denotes a rotary shaft connected to the engine output shaft 3 as a rotary transmission system for operating the respective pistons 9a, 9b, 9c in conjunction with each other.
a first crank 14a connecting the piston 9a of the low temperature cylinder chamber 8a and a second crank 14b connecting the piston 9b of the medium temperature cylinder chamber 8b in order from the connection side with the engine output shaft 3 in accordance with the arrangement of the a, 8b and 8c. , The third crank 14c connecting the piston 9c of the high-temperature cylinder chamber 8c
Is provided.
【００３６】各シリンダ室８ａ，８ｂ，８ｃは、回転軸
周りでの相互の姿勢関係（換言すれば、回転軸周りにお
けるピストン往復動作方向の相互角度関係）を所定の関
係に固定して配置してあり、また、低温シリンダ室８ａ
に対する第１クランク１４ａと中温シリンダ室８ｂに対
する第２クランク１４ｂとは、互いの回転位相差を所定
角度に固定して回転軸１３に形成してあり、これらシリ
ンダ室についての姿勢関係の設定、及び、第１クランク
１４ａと第２クランク１４ｂとについての回転位相差の
設定により、中温シリンダ室８ｂのピストン９ｂは、低
温シリンダ室８ａのピストン９ａよりも常に一定の位相
遅れをもって往復動作するように、換言すれば、中温シ
リンダ室８ｂが低温シリンダ室８ａよりも常に一定の位
相遅れ（例えば、１／４周期程度の位相遅れ）をもって
作動ガスＧの吐出と吸入を行うように構成してある。The respective cylinder chambers 8a, 8b, 8c are arranged such that their mutual attitude relationship around the rotation axis (in other words, the mutual angle relationship of the piston reciprocating operation direction around the rotation axis) is fixed at a predetermined relationship. And the low-temperature cylinder chamber 8a
And the second crank 14b for the medium-temperature cylinder chamber 8b are formed on the rotating shaft 13 with the rotational phase difference fixed at a predetermined angle, and the attitude relationship for these cylinder chambers is set, and By setting the rotational phase difference between the first crank 14a and the second crank 14b, the piston 9b of the medium-temperature cylinder chamber 8b reciprocates with a constant phase delay more than the piston 9a of the low-temperature cylinder chamber 8a. In other words, the medium-temperature cylinder chamber 8b always discharges and sucks the working gas G with a constant phase delay (for example, a phase delay of about 1/4 cycle) than the low-temperature cylinder chamber 8a.
【００３７】一方、回転軸１３は、上記の第１クランク
１４ａ及び第２クランク１４ｂを設けるエンジン連結側
の回転軸１３ｍと、第３クランク１４ｃを設ける端部側
の回転軸１３ｎとに分割し、この分割部には図２及び図
３に示す如き差動機構１５を介装してあり、また、この
差動機構１５を差動機能停止させた伝動状態として上記
の両回転軸１３ｍ，１３ｎを互いに等しい角速度で連動
回転させる軸関係保持操作と、差動機構１５を差動機能
させて両回転軸１３ｍ，１３ｎを互いに異なる角速度で
所要角度だけ相対回転動作させる軸関係変更操作とを行
う軸関係操作手段２０を設けてある。On the other hand, the rotating shaft 13 is divided into a rotating shaft 13m on the engine connection side where the first crank 14a and the second crank 14b are provided, and a rotating shaft 13n on the end portion where the third crank 14c is provided. A differential mechanism 15 as shown in FIG. 2 and FIG. 3 is interposed in this divided portion, and the two rotary shafts 13m and 13n are set in a transmission state in which the differential mechanism 15 is stopped in a differential function. An axial relationship for performing an axial relationship maintaining operation of interlocking rotation at an equal angular velocity and an axial relationship changing operation of causing the differential mechanism 15 to perform a differential function and relatively rotating the two rotating shafts 13m and 13n by a required angle at mutually different angular velocities. An operating means 20 is provided.
【００３８】つまり、上記の差動機構１５、及び、軸関
係操作手段２０は（図１ないし図４参照）、高温シリン
ダ室８ｃのピストン９ｃと他のシリンダ室８ａ，８ｂに
対するピストン９ａ，９ｂとのピストン位相差関係を調
整するものであり、前記の軸関係保持操作では、差動機
構１５を差動機能停止させた伝動状態として両回転軸１
３ｍ，１３ｎを互いに等しい角速度で連動回転させるこ
とにより、両回転軸１３ｍ，１３ｎの回転位相関係（換
言すれば、高温シリンダ室８ｃに対するクランク１４ｃ
と他のシリンダ室８ａ，８ｂに対するクランク１４ａ，
１４ｂとの回転位相差関係）を一定に保った回転伝動状
態とし、これにより、高温シリンダ室８ｃのピストン９
ｃと他のシリンダ室８ａ，８ｂに対するピストン９ａ，
９ｂとを一定のピストン位相差関係で動作させる、すな
わち、高温シリンダ室８ｃと他のシリンダ室８ａ，８ｂ
とを一定の吐出吸入動作関係で作動ガス吐出吸入させる
状態として、機器特性を一定に保った運転を行う。That is, the differential mechanism 15 and the shaft-related operating means 20 (see FIGS. 1 to 4) are provided with the piston 9c for the high-temperature cylinder chamber 8c and the pistons 9a and 9b for the other cylinder chambers 8a and 8b. In the above-described axial relationship maintaining operation, the two rotary shafts 1 are set in a transmission state in which the differential mechanism 15 has stopped the differential function.
3m and 13n are interlockedly rotated at the same angular velocity, so that the rotational phase relationship between the two rotating shafts 13m and 13n (in other words, the crank 14c with respect to the high temperature cylinder chamber 8c)
And the cranks 14a for the other cylinder chambers 8a and 8b,
14b) is kept in a rotational transmission state in which the piston 9 in the high temperature cylinder chamber 8c is
c and the pistons 9a, 9b for the other cylinder chambers 8a, 8b.
9b is operated in a fixed piston phase difference relationship, that is, the high-temperature cylinder chamber 8c and the other cylinder chambers 8a and 8b
Are operated in such a manner that the working gas is discharged and sucked in a constant discharge and suction operation relation, and the operation is performed while keeping the device characteristics constant.
【００３９】これに対し、前記の軸関係変更操作では、
差動機構１５を差動機能させて両回転軸１３ｍ，１３ｎ
を互いに異なる角速度で所要角度だけ相対回転動作させ
ることにより、これら回転軸１３ｍ，１３ｎの回転位相
関係（換言すれば、高温シリンダ室８ｃに対するクラン
ク１４ｃと他のシリンダ室８ａ，８ｂに対するクランク
１４ａ，１４ｂとの回転位相差関係）を所要角度だけ変
更し、これにより、高温シリンダ室８ｃのピストン９ｃ
と他のシリンダ室８ａ，８ｂに対するピストン９ａ，９
ｂとのピストン位相差関係を変更する。On the other hand, in the above-mentioned axis relation changing operation,
The differential mechanism 15 is caused to function as a differential so that the two rotating shafts 13m and 13n
Are rotated relative to each other by a required angle at different angular velocities, so that the rotational phase relationship between the rotating shafts 13m and 13n (in other words, the crank 14c for the high-temperature cylinder chamber 8c and the cranks 14a and 14b for the other cylinder chambers 8a and 8b). Is changed by the required angle, thereby the piston 9c of the high-temperature cylinder chamber 8c is changed.
And pistons 9a, 9 for the other cylinder chambers 8a, 8b.
Change the piston phase difference relationship with b.
【００４０】すなわち、機器特性の変更を要する場合、
上記の軸関係変更操作によりピストン位相差関係を変更
した上で、軸関係保持操作を行って、両回転軸１３ｍ，
１３ｎを変更後の回転位相関係に保った状態で連動回転
させることにより、高温シリンダ室８ｃのピストン９ｃ
と他のシリンダ室８ａ，８ｂに対するピストン９ａ，９
ｂとを変更後のピストン位相差関係に保った状態で動作
させて、高温シリンダ室８ｃと他のシリンダ室８ａ，８
ｂとを変更後のピストン位相差関係に対応する新たな吐
出吸入動作関係で作動ガス吐出吸入させ、これにより、
機器特性を変更した運転を行う。That is, when it is necessary to change the device characteristics,
After changing the piston phase difference relationship by the above-described shaft relationship changing operation, the shaft relationship maintaining operation is performed to perform the both rotation shafts 13m,
13n is rotated in an interlocked state while maintaining the changed rotational phase relationship, whereby the piston 9c of the high-temperature cylinder chamber 8c is rotated.
And pistons 9a, 9 for the other cylinder chambers 8a, 8b.
b is operated in a state where the piston phase difference relationship after the change is maintained, and the high-temperature cylinder chamber 8c and the other cylinder chambers 8a, 8c are operated.
b and the working gas is discharged and suctioned in a new discharge and suction operation relationship corresponding to the piston phase difference relationship after the change.
Perform operation with changed device characteristics.
【００４１】エンジン連結側の回転軸１３ｍと端部側の
回転軸１３ｎとの間には、差動機構１５に加え、前記の
軸関係保持操作において伝動作用状態とし、かつ、前記
の軸関係変更操作において伝動遮断状態とするクラッチ
機構２１を、差動機構１５とは伝動上で並列の関係で介
装してあり、両回転軸１３ｍ，１３ｎを互いに等しい角
速度で連動回転させる軸関係保持操作においては、この
クラッチ機構２１を伝動作用状態にして、差動機構１５
とは並列の関係のクラッチ機構２１を介しての両回転軸
１３ｍ，１３ｎにわたる回転伝動を行わせることによ
り、両回転軸１３ｍ，１３ｎにわたる回転伝動上で差動
機構１５の構成ギア１６，１６ａ，１８，１７ａ，１７
に作用する回転トルクを軽減するようにしてある。Between the rotating shaft 13m on the engine connection side and the rotating shaft 13n on the end side, in addition to the differential mechanism 15, a transmission operation state is established in the above-described axial relationship maintaining operation, and the axial relationship change is performed. A clutch mechanism 21, which is in a transmission cutoff state in operation, is interposed in a transmission-parallel relationship with the differential mechanism 15, and in a shaft relation maintaining operation in which the two rotating shafts 13m and 13n are interlocked and rotated at an equal angular velocity. Puts the clutch mechanism 21 in the transmission operation state and sets the differential mechanism 15
And the transmission gears 16 and 16a of the differential mechanism 15 on the rotation transmission over both the rotating shafts 13m and 13n through the clutch mechanism 21 in a parallel relationship. 18, 17a, 17
To reduce the rotational torque acting on the motor.
【００４２】また、差動機構１５の差動機能により両回
転軸１３ｍ，１３ｎを互いに異なる角速度で相対回転動
作させる軸関係変更操作においては、このクラッチ機構
２１を伝動遮断状態とすることにより、両回転軸１３
ｍ，１３ｎの互いに異なる角速度での相対回転動作を許
容する。In the axial relationship changing operation for causing the two rotating shafts 13m and 13n to perform relative rotation at different angular velocities by the differential function of the differential mechanism 15, the clutch mechanism 21 is set to the power transmission cutoff state to allow the two shafts 13m and 13n to rotate. Rotating shaft 13
m and 13n are allowed to rotate at different angular velocities.
【００４３】なお、本例においては、クラッチ機構２１
に対する専用操作機構を設け、この専用操作機構により
クラッチ機構２１を伝動作用状態と伝動遮断状態とに適
時切り換え操作するものとする。In this embodiment, the clutch mechanism 21
, And the clutch mechanism 21 is appropriately switched between the transmission operation state and the transmission cutoff state by the dedicated operation mechanism.
【００４４】差動機構１５には、エンジン連結側の回転
軸１３ｍと一体回転（すなわち、第１及び第２クランク
１４ａ，１４ｂと一体回転）する第１ギア１６と、端部
側の回転軸１３ｎと一体回転（すなわち、第３クランク
１４ｃと一体回転）する第２ギア１７と、位置固定され
た状態で第１ギア１６に咬合する複数個の第１遊星ギア
１６ａと、第２ギア１７に咬合する複数個の第２遊星ギ
ア１７ａと、第２ギア１７の周りでの第２遊星ギア１７
ａの位置変更にかかわらず第１遊星ギア１６ａ及び第２
遊星ギア１７ａの両方に対して咬合する内歯式の中間ギ
ア１８とを備える遊星ギア式差動機構を採用してあり、
前記のクラッチ機構２１は、互いに同方向に回転する第
１ギア１６と第２ギア１７との間に配置して、両回転軸
１３ｍ，１３ｎ間に介装してある。The differential mechanism 15 includes a first gear 16 that rotates integrally with the rotating shaft 13m on the engine connection side (that is, rotates integrally with the first and second cranks 14a and 14b), and a rotating shaft 13n on the end side. A second gear 17 integrally rotating with the third gear 14c (i.e., integrally rotating with the third crank 14c); a plurality of first planetary gears 16a meshing with the first gear 16 in a fixed state; A plurality of second planetary gears 17a and a second planetary gear 17 around the second gear 17
The first planetary gear 16a and the second planetary gear 16a
A planetary gear type differential mechanism including an internal gear type intermediate gear 18 meshing with both of the planetary gears 17a,
The clutch mechanism 21 is disposed between the first gear 16 and the second gear 17 that rotate in the same direction, and is interposed between the rotating shafts 13m and 13n.
【００４５】なお、第１ギア１６と第１遊星ギア１６ａ
とのギア比は、第２ギア１７と第２遊星ギア１７ａとの
ギア比に等しくし、また、第１遊星ギア１６ａと中間ギ
ア１８とのギア比は、第２遊星ギア１７ａと中間ギア１
８とのギア比に等しくしてある。The first gear 16 and the first planetary gear 16a
And the gear ratio between the first planetary gear 16a and the intermediate gear 18 is equal to the gear ratio between the second gear 17 and the second planetary gear 17a.
The gear ratio is set equal to 8.
【００４６】また、前記の軸関係操作手段２０として
は、複数個の第２遊星ギア１７ａを支持する可動キャリ
ア１９を回転させることにより、複数個の第２遊星ギア
１７ａを同時に第２ギア１７の周りで位置変更操作する
とともに、変更位置で固定する機能を有するウォームギ
ア式操作機構を採用してある。As the shaft-related operation means 20, the plurality of second planetary gears 17a are simultaneously rotated by rotating the movable carrier 19 supporting the plurality of second planetary gears 17a. A worm gear-type operation mechanism having a function of changing the position around and fixing at the changed position is adopted.
【００４７】つまり、ウォームギア式操作機構２０の固
定機能により第２遊星ギア１７ａの位置を第２ギア１７
の周りで固定し、これにより、差動を伴わない形態の回
転伝動を第１ギア１６、第１遊星ギア１６ａ、中間ギア
１８、第２遊星ギア１７ａ、第２ギア１７にわたり行わ
せることで、両回転軸１３ｍ，１３ｎを互いに等しい角
速度で互いに同方向に連動回転させる状態とし、これを
もって、前記の軸関係保持操作とする。That is, the position of the second planetary gear 17a is changed by the fixing function of the worm gear type operation mechanism 20 to the second gear 17a.
Around the first gear 16, the first planetary gear 16a, the intermediate gear 18, the second planetary gear 17a, and the second gear 17 by performing rotation transmission in a form without differential. The two rotation shafts 13m and 13n are interlockedly rotated in the same direction at the same angular velocity, and this is the above-mentioned axial relationship maintaining operation.
【００４８】また、ウォームギア式操作機構２０により
第２遊星ギア１７ａの位置を第２ギア１７の周りで変更
操作して、この位置変更過程で、第１ギア１６、第１遊
星ギア１６ａ、中間ギア１８、第２遊星ギア１７ａ、第
２ギア１７にわたる回転伝動に差動を生じさせることに
より、第２ギア１７の周りでの第２遊星ギア１７ａの位
置変更角度分だけ、第２遊星ギア１７ａの位置変更に伴
い両回転軸１３ｍ，１３ｎを互いに異なる角速度で相対
回転動作させ、これをもって、前記の軸関係変更操作と
する。Further, the position of the second planetary gear 17a is changed around the second gear 17 by the worm gear type operation mechanism 20, and in this position changing process, the first gear 16, the first planetary gear 16a, the intermediate gear 18, by causing a differential in the rotation transmission across the second planetary gear 17a and the second gear 17, the position of the second planetary gear 17a is changed by the position change angle of the second planetary gear 17a around the second gear 17. With the position change, the two rotation shafts 13m and 13n are relatively rotated at different angular velocities, and this is the above-mentioned axial relationship change operation.
【００４９】次に機器運転については、高温シリンダ室
８ｃのピストン９ｃと中温シリンダ室８ｂのピストン９
ｂと低温シリンダ室８ａのピストン９ａを前記の軸関係
保持操作により所定のピストン位相差関係に保持して動
作させる状態で、高温加熱器１２ｃ、中温放熱器１２
ｂ、低温吸熱器１２ａ、並びに、各再生熱交換器１１
ｍ，１１ｎの作用下において、エンジン１から回転軸１
３に回転動力を付与することにより、ガス連通路１０に
よる連通下で個別に作動ガス吐出吸入を行う３つのシリ
ンダ室８ａ，８ｂ，８ｃのうち、中温シリンダ室８ｂと
低温シリンダ室８ａとの対については、回転軸１３の回
転動力により、低温シリンダ室８ａを吸熱作用させると
ともに中温シリンダ室８ｂを放熱作用させて熱の汲み上
げを行う逆スターリングサイクルの冷凍機ないしヒート
ポンプとして機能させる。Next, regarding the operation of the equipment, the piston 9c of the high-temperature cylinder chamber 8c and the piston 9 of the medium-temperature cylinder chamber 8b will be described.
b and the piston 9a of the low-temperature cylinder chamber 8a are maintained in a predetermined piston phase difference relationship by the above-mentioned axial relationship maintaining operation, and the high-temperature heater 12c and the intermediate-temperature radiator 12c are operated.
b, low-temperature heat absorber 12a and each regenerative heat exchanger 11
Under the action of m, 11n, the rotation shaft 1
By applying rotational power to the third cylinder chamber 3, the three cylinder chambers 8 a, 8 b, and 8 c that individually discharge and inhale the working gas under the communication of the gas communication path 10 are paired with the medium-temperature cylinder chamber 8 b and the low-temperature cylinder chamber 8 a. With respect to the above, the low-temperature cylinder chamber 8a is made to absorb heat and the medium-temperature cylinder chamber 8b is made to radiate heat by the rotational power of the rotating shaft 13 to function as a refrigerator or heat pump of an inverse Stirling cycle for pumping up heat.
【００５０】また、これに並行して、高温シリンダ室８
ｃと中温シリンダ室８ｂとの対については、高温加熱器
１２ｃから高温シリンダ室８ｃへのエンジン排ガス保有
熱の入力より、中温シリンダ室８ｂでの放熱を伴いなが
ら回転動力を発生するスターリングサイクル・エンジン
として機能させ、この発生動力をエンジン１から回転軸
１３への動力付与に付加する形態で回転軸１３に与え
る。At the same time, the high-temperature cylinder chamber 8
For the pair of the cylinder c and the medium-temperature cylinder chamber 8b, a Stirling cycle engine that generates rotational power while radiating heat in the medium-temperature cylinder chamber 8b based on the input of engine exhaust gas possession heat from the high-temperature heater 12c to the high-temperature cylinder chamber 8c. And the generated power is given to the rotating shaft 13 in a form added to the application of power from the engine 1 to the rotating shaft 13.
【００５１】すなわち、各シリンダ室８ａ，８ｂ，８ｃ
の作動ガス吐出吸入に伴い、各シリンダ室８ａ，８ｂ，
８ｃにわたる作動ガスＧの圧縮と膨張、及び、シリンダ
室間での作動ガス移動を生じさせることにおいて、高温
シリンダ室８ｃと中温シリンダ室８ｂとの対については
基本的に、圧縮された作動ガスＧが高温シリンダ室側の
再生熱交換器１１ｎを通じ、この再生熱交換器１１ｎの
蓄熱温熱による加熱を受けて高温シリンダ室８ｃに導入
され、その後、この作動ガスＧが膨張過程を経て高温加
熱器１２ｃにより加熱され、続いて、この作動ガスＧが
再び高温シリンダ室側の再生熱交換器１１ｎを通じ、そ
の再生熱交換器１１ｎへの温熱蓄熱と自身の温度降下を
伴い高温シリンダ室８ｃから中温シリンダ室８ｂへ導出
され、さらに、この温度降下した作動ガスＧが、圧縮過
程を経て高温シリンダ室８ｃの温度レベルよりも低い中
温レベルで中温放熱器１２ｂに対し放熱（すなわち、温
熱媒Ｈを加温）する、といったスターリングサイクルを
実行させ、これにより動力を発生させる。That is, each cylinder chamber 8a, 8b, 8c
Of each cylinder chamber 8a, 8b,
In causing the compression and expansion of the working gas G over 8c and the movement of the working gas between the cylinder chambers, the pair of the high temperature cylinder chamber 8c and the medium temperature cylinder chamber 8b basically has the compressed working gas G Is heated by the heat stored in the regenerative heat exchanger 11n through the regenerative heat exchanger 11n on the high-temperature cylinder chamber side and is introduced into the high-temperature cylinder chamber 8c. After that, the working gas G is expanded through the high-temperature heater 12c. Then, the working gas G passes through the regenerative heat exchanger 11n on the high-temperature cylinder chamber side again, and stores the heat stored in the regenerative heat exchanger 11n and its own temperature drop from the high-temperature cylinder chamber 8c to the medium-temperature cylinder chamber. 8b, and the working gas G whose temperature has dropped is discharged through the compression process at a medium temperature level lower than the temperature level of the high temperature cylinder chamber 8c. Radiating to vessel 12b (i.e., the heat medium H warming) is, to execute the Stirling cycle such, thereby to generate power.
【００５２】また、中温シリンダ室８ｂと低温シリンダ
室８ｃとの対については基本的に、圧縮された作動ガス
Ｇが低温シリンダ室側の再生熱交換器１１ｍを通じ、こ
の再生熱交換器１１ｍの蓄熱冷熱による冷却を受けて低
温シリンダ室８ａに導入され、その後、この作動ガスＧ
が膨張過程を経て低温吸熱器１２ａに対し吸熱（すなわ
ち、冷熱媒Ｃを冷却）し、続いて、この作動ガスＧが再
び低温シリンダ室側の再生熱交換器１１ｍを通じ、その
再生熱交換器１１ｍへの冷熱蓄熱と自身の温度上昇を伴
い低温シリンダ室８ａから中温シリンダ室８ｂへ導出さ
れ、さらに、この温度上昇した作動ガスＧが、圧縮過程
を経て低温シリンダ室８ａの温度レベルよりも高い中温
レベルで中温放熱器１２ｂに対し放熱（すなわち、温熱
媒Ｈを加温）する、といった逆スターリングサイクルを
実行させ、これにより、熱を汲み上げる冷凍機機能ない
しヒートポンプ機能を得る。In the pair of the medium-temperature cylinder chamber 8b and the low-temperature cylinder chamber 8c, basically, the compressed working gas G passes through the regenerative heat exchanger 11m on the low-temperature cylinder chamber side to store heat in the regenerative heat exchanger 11m. After being cooled by cold heat, it is introduced into the low-temperature cylinder chamber 8a.
Absorbs heat (that is, cools the cooling medium C) into the low-temperature heat absorber 12a through the expansion process, and then the working gas G flows again through the regenerative heat exchanger 11m on the low-temperature cylinder chamber side, and the regenerative heat exchanger 11m The working gas G is discharged from the low-temperature cylinder chamber 8a to the medium-temperature cylinder chamber 8b with the cold heat storage and its own temperature rise, and the temperature-raised working gas G passes through the compression process and has a medium temperature higher than the temperature level of the low-temperature cylinder chamber 8a. A reverse Stirling cycle of radiating heat (that is, heating the heating medium H) to the medium temperature radiator 12b at the level is executed, thereby obtaining a refrigerator function or a heat pump function of pumping heat.
【００５３】そして、上記の運転において冷凍機ないし
ヒートポンプとしての熱負荷条件の変化・変更、あるい
は、エンジン動力やエンジン排熱量についてのエンジン
側運転条件の変化・変更があって機器特性の変更を要す
る場合には、前述の如く、軸関係変更操作としてクラッ
チ機構２１を伝動遮断状態にした上でウォームギア式操
作機構２０により第２遊星ギア１７ａの位置を変更操作
して、高温シリンダ室８ｃのピストン９ｃと他のシリン
ダ室８ａ，８ｂのピストン９ａ，９ｂとのピストン位相
差関係を変更し、その上で、軸関係保持操作としてウォ
ームギア式操作機構２０の固定機能により第２遊星ギア
１７ａを変更位置に固定するとともに、クラッチ機構２
１を伝動作用状態にすることにより、高温シリンダ室８
ｃのピストン９ｃと他のシリンダ室８ａ，８ｂのピスト
ン９ａ，９ｂとを変更後の新たなピストン位相差関係に
保持した状態で動作させて、高温シリンダ室８ｃと他の
シリンダ室８ａ，８ｂとを変更後のピストン位相差関係
に対応する新たな吐出吸入動作関係で作動ガス吐出吸入
させるようにし、これにより、機器特性を新たな熱負荷
条件や新たなエンジン側運転条件に適合するものに変更
した運転、例えば、エンジン動力の必要入力量、エンジ
ン排熱の必要入力量（すなわち高温加熱器１２ｃの必要
加熱量）、中温放熱器１２ｂの放熱量、及び、低温吸熱
器１２ａの吸熱量についての比を新たな熱負荷条件や新
たなエンジン側運転条件に適合するものに変更した運転
や、あるいは、エンジン排ガスの必要温度（すなわち、
高温加熱器１２ｃの必要加熱温度）、中温放熱器１２ｂ
の放熱温度、及び、低温吸熱器１２ａの吸熱温度につい
ての比を新たな熱負荷条件や新たなエンジン側運転条件
に適合するものに変更した運転を実施する。In the above operation, there is a change or change in the heat load condition of the refrigerator or the heat pump, or a change or change in the engine side operation condition of the engine power or the engine exhaust heat, so that the device characteristics need to be changed. In this case, as described above, after the clutch mechanism 21 is set to the transmission cutoff state as the axial relation changing operation, the position of the second planetary gear 17a is changed by the worm gear type operating mechanism 20, and the piston 9c of the high temperature cylinder chamber 8c is changed. And the piston phase differences between the pistons 9a and 9b of the other cylinder chambers 8a and 8b are changed, and the second planetary gear 17a is moved to the changed position by the fixing function of the worm gear type operation mechanism 20 as the axial relation maintaining operation. Fixing and clutch mechanism 2
By setting 1 to the state for power transmission, the high-temperature cylinder chamber 8
c and the other pistons 9a and 9b of the other cylinder chambers 8a and 8b are operated while maintaining the new piston phase difference relationship after the change, so that the high temperature cylinder chamber 8c and the other cylinder chambers 8a and 8b Of the working gas discharge and suction in accordance with the new discharge / suction operation relationship corresponding to the piston phase difference relationship after the change, thereby changing the device characteristics to those that match the new heat load condition and the new engine side operating condition Operation, for example, the required input amount of the engine power, the required input amount of the engine exhaust heat (that is, the required heating amount of the high-temperature heater 12c), the heat radiation amount of the medium-temperature radiator 12b, and the heat absorption amount of the low-temperature heat absorber 12a. Operating the ratio to meet new heat load conditions or new engine side operating conditions, or the required engine exhaust gas temperature (ie,
Required heating temperature of high temperature heater 12c), medium temperature radiator 12b
The operation is performed in which the ratio between the heat radiation temperature and the heat absorption temperature of the low-temperature heat absorber 12a is changed to one that matches the new heat load condition and the new engine-side operation condition.
【００５４】〔別実施例〕次に別実施例を列記する。[Another Embodiment] Next, another embodiment will be described.
【００５５】前述の実施例の如くクラッチ機構２１を専
用操作手段により外部から切り換え操作するに代え、ク
ラッチ機構２１として、回転に伴い自動的に伝動作用状
態に切り換わり、かつ、回転停止に伴い自動的に伝動遮
断状態に切り換わる遠心式等の自動クラッチ機構を採用
してもよい。Instead of switching the clutch mechanism 21 from the outside by the dedicated operation means as in the above-described embodiment, the clutch mechanism 21 is automatically switched to the transmission operation state as it rotates and automatically as the rotation stops. An automatic clutch mechanism of a centrifugal type or the like that switches to the transmission cutoff state may be employed.
【００５６】つまり、このような自動クラッチを採用す
る場合には、回転運転を停止（前述の実施例ではエンジ
ン１を停止）して両回転軸１３ｍ，１３ｎの連動回転を
停止することにより、この回転停止に伴い自動クラッチ
機構２１を伝動作用状態から伝動遮断状態に自動的に切
り換わり動作させて、両回転軸１３ｍ，１３ｎの互いに
異なる角速度での相対回転動作を許す状態とし、この状
態で、軸関係変更操作を行うことにより、差動による両
回転軸１３ｍ，１３ｎの相対回転動作として、両回転軸
１３ｍ，１３ｎのうちの一方は回転停止させたままで他
方を回転動作させ、これにより、両回転軸１３ｍ，１３
ｎの回転位相関係を変更する。That is, when such an automatic clutch is employed, the rotation operation is stopped (in the above-described embodiment, the engine 1 is stopped) to stop the interlocking rotation of the two rotating shafts 13m and 13n. When the rotation is stopped, the automatic clutch mechanism 21 is automatically switched from the transmission operation state to the transmission cutoff state to operate, so that the two rotation shafts 13m and 13n are allowed to perform a relative rotation operation at different angular velocities. By performing the axial relationship changing operation, as one of the relative rotation operations of the two rotating shafts 13m and 13n due to the differential, one of the two rotating shafts 13m and 13n is rotated while the other is stopped, whereby the two rotating shafts 13m and 13n are rotated. Rotating shaft 13m, 13
Change the rotational phase relationship of n.
【００５７】また、軸関係保持操作を行った状態で回転
運転を再開（前述の実施例ではエンジン１の運転を再
開）して、差動構造１５の伝動作用により両回転軸１３
ｍ，１３ｎを連動回転させるようにしながら、この回転
開始に伴い自動クラッチ機構２１を伝動遮断状態から伝
動作用状態に自動的に切り換わり動作させ、これによ
り、クラッチ機構２１を介しての両回転軸１３ｍ，１３
ｎにわたる回転伝動を再開させた状態で、両回転軸１３
ｍ，１３ｎを互いに等しい角速度で互いの回転位相関係
を保って連動回転させる。In addition, the rotation operation is resumed (the operation of the engine 1 is resumed in the above-described embodiment) in a state where the shaft relation maintaining operation is performed, and the two rotation shafts 13 are used for the transmission operation of the differential structure 15.
The automatic clutch mechanism 21 is automatically switched from the transmission cut-off state to the transmission operation state in accordance with the start of the rotation, and the two rotating shafts via the clutch mechanism 21 are operated. 13m, 13
n while the rotation transmission over n
m and 13n are interlockedly rotated at an equal angular velocity while maintaining a mutual rotational phase relationship.
【００５８】クラッチ機構２１の切り換え操作について
は、更に、図５に示すように、軸関係操作手段２０とク
ラッチ機構２１とを連係動作させる連係操作手段２２を
設け、この連係操作手段２２の連係機能により、軸関係
保持操作においてクラッチ機構２１を伝動作用状態に
し、また、軸関係変更操作においてクラッチ機構２１を
伝動遮断状態にする構成を採用してもよい。As for the switching operation of the clutch mechanism 21, as shown in FIG. 5, there is further provided a link operation means 22 for linking the shaft-related operation means 20 and the clutch mechanism 21, and the link function of the link operation means 22 is provided. Accordingly, a configuration may be adopted in which the clutch mechanism 21 is set to the transmission operation state in the shaft relation maintaining operation, and the clutch mechanism 21 is set to the transmission cutoff state in the shaft relation changing operation.
【００５９】そして、この連係操作手段２２の具体的形
式としては、例えば、軸関係操作手段２０に対する操作
状態検出に基づいて、軸関係操作手段２０が軸関係保持
操作状態になったとき（すなわち、前述の実施例ではウ
ォームギア式操作機構２０の回転操作が停止されたと
き）に、クラッチ機構２１を伝動作用状態に切り換え操
作し、かつ、軸関係操作手段２０が軸関係変更操作状態
になったとき（すなわち、前述の実施例ではウォームギ
ア式操作機構２０の回転操作が開始されたとき）に、ク
ラッチ機構２１を伝動遮断状態に切り換え操作するとい
った形式、あるいは、軸関係保持指令が付与されること
に対する制御動作として、軸関係操作手段２０に軸関係
保持操作を行わせるとともにクラッチ機構２１を伝動作
用状態に切り換え操作し、かつ、軸関係変更指令が付与
されることに対する制御動作として、クラッチ機構２１
を伝動遮断状態に切り換え操作するとともに軸関係操作
手段２０に軸関係変更操作を行わせるといった形式を採
用できる。The specific form of the link operation means 22 is, for example, when the axis relation operation means 20 enters the axis relation holding operation state based on the detection of the operation state of the axis relation operation means 20 (ie, In the above-described embodiment, when the rotation operation of the worm gear type operation mechanism 20 is stopped), the clutch mechanism 21 is switched to the transmission operation state, and the axis relation operation means 20 is in the axis relation change operation state. (That is, in the above-described embodiment, when the rotation operation of the worm gear type operation mechanism 20 is started, the clutch mechanism 21 is switched to the transmission cutoff state, or when the shaft relation holding command is given. As a control operation, the shaft-related operation means 20 is caused to perform a shaft-related holding operation, and the clutch mechanism 21 is switched to a transmission operation state. And, and, as a control operation for the axial relationship change command is given, the clutch mechanism 21
Can be employed to switch the transmission to the transmission cutoff state, and to cause the axis-related operation means 20 to perform an axis-related change operation.
【００６０】差動機構１５には遊星ギア式に限らず種々
の形式のものを採用でき、また、軸関係操作手段２０の
具体的構造も、採用する差動機構１５の形式等に応じて
種々の構成変更が可能である。The differential mechanism 15 is not limited to the planetary gear type, and various types can be employed. The specific structure of the shaft-related operation means 20 also varies depending on the type of the differential mechanism 15 to be employed. Configuration change is possible.
【００６１】前述の実施例の如き遊星ギア式差動機構１
５を採用するにあたり、一方側の回転軸１３ｍとともに
回転させる第１ギア１６、及び、他方側の回転軸１３ｎ
とともに回転させる第２ギア１７は夫々、対応の回転軸
１３ｍ，１３ｎに対し直接に連結する構成に限定される
ものではなく、第１ギア１６とこれに対応する一方側の
回転軸１３ｍとの間や、第２ギア１７とこれに対応する
他方側の回転軸１３ｎとの間に適当なギア伝動構造を介
装する構成を採用してもよい。The planetary gear type differential mechanism 1 as in the above-described embodiment.
5, the first gear 16 that rotates together with the rotation shaft 13m on one side, and the rotation shaft 13n on the other side
The second gear 17 to be rotated together with the first gear 16 is not limited to a configuration directly connected to the corresponding rotation shafts 13m and 13n, respectively. Alternatively, a configuration may be adopted in which an appropriate gear transmission structure is interposed between the second gear 17 and the corresponding rotating shaft 13n on the other side.
【００６２】一方側の回転軸１３ｍと他方側の回転軸１
３ｎとの回転位相関係を変更する目的は、前述の実施例
の如きピストン位相差関係の変更に限定されるものでな
なく、また、本発明による可変位相装置の利用分野もス
ターリングサイクル機器に限定されるものではなく、回
転伝動を用いる各種分野の機器において本発明を適用で
きる。The rotating shaft 13m on one side and the rotating shaft 1 on the other side
The purpose of changing the rotational phase relationship with 3n is not limited to the change of the piston phase difference relationship as in the above-described embodiment, and the field of use of the variable phase device according to the present invention is also limited to Stirling cycle equipment. However, the present invention can be applied to devices in various fields using rotary transmission.
【００６３】尚、特許請求の範囲の項に図面との対照を
便利にするため符号を記すが、該記入により本発明は添
付図面の構成に限定されるものではない。Incidentally, reference numerals are written in the claims for convenience of comparison with the drawings, but the present invention is not limited to the configuration of the attached drawings by the entry.
【図１】エンジン駆動式冷凍機ないしヒートポンプの構
成図FIG. 1 is a configuration diagram of an engine-driven refrigerator or heat pump.
【図２】要部の側面視構造図FIG. 2 is a side view structural view of a main part.
【図３】要部の軸芯方向視構造図FIG. 3 is a structural view of an essential part as viewed in an axial direction.
【図４】熱機器部の軸芯方向視構造図FIG. 4 is a structural view of the thermal equipment section as viewed in the axial direction.
【図５】別実施例を示す側面視構造図FIG. 5 is a side view structural view showing another embodiment.
【図６】従来装置の構造図FIG. 6 is a structural view of a conventional device.
１３ｍ，１３ｎ 回転軸 １５ 差動機構 ２０ 軸関係操作手段 ２１ クラッチ機構 １６ 第１ギア １７ 第２ギア １６ａ 第１遊星ギア １７ａ 第２遊星ギア １８ 中間ギア ２２ 連係操作手段 13m, 13n Rotating shaft 15 Differential mechanism 20 Axis-related operation means 21 Clutch mechanism 16 First gear 17 Second gear 16a First planetary gear 17a Second planetary gear 18 Intermediate gear 22 Linking operation means
フロントページの続き (72)発明者 森川 和之 兵庫県尼崎市浜１丁目１番１号 株式会 社クボタ 技術開発研究所内 (72)発明者 福井 哲 大阪府堺市石津北町64番地 株式会社ク ボタ 堺製造所内 (56)参考文献 特開 平１−303318（ＪＰ，Ａ) 特開 昭60−125442（ＪＰ，Ａ) 特開 平１−283448（ＪＰ，Ａ) (58)調査した分野(Int.Cl.7，ＤＢ名) F16D 1/12 F25B 9/14 F16H 1/28 Continued on the front page (72) Inventor Kazuyuki Morikawa 1-1-1 Hama, Amagasaki-shi, Hyogo Prefecture Inside Kubota R & D Laboratories Co., Ltd. (56) References JP-A-1-303318 (JP, A) JP-A-60-125442 (JP, A) JP-A-1-283448 (JP, A) (58) Fields investigated (Int. . 7, DB name) F16D 1/12 F25B 9/14 F16H 1/28
Claims (4)
転軸（１３ｎ）との間に差動機構（１５）を介装し、 この差動機構（１５）を差動機能停止させた伝動状態と
して前記の両回転軸（１３ｍ），（１３ｎ）を互いに等
しい角速度で連動回転させる軸関係保持操作と、前記差
動機構（１５）を差動機能させて前記の両回転軸（１３
ｍ），（１３ｎ）を互いに異なる角速度で所要角度だけ
相対回転動作させる軸関係変更操作とを行う軸関係操作
手段（２０）を設けた可変位相装置であって、 前記の軸関係保持操作において伝動作用状態とし、か
つ、前記の軸関係変更操作において伝動遮断状態とする
クラッチ機構（２１）を、前記差動機構（１５）とは並
列の関係で前記両回転軸（１３ｍ），（１３ｎ）の間に
介装した可変位相装置。1. A differential mechanism (15) is interposed between a rotating shaft (13m) on one side and a rotating shaft (13n) on the other side, and the differential function (15) is stopped. In the transmission state, the two rotation shafts (13m) and (13n) are rotated in association with each other at an equal angular velocity, and the differential mechanism (15) is caused to function as a differential so that the two rotation shafts (13m) and (13n) are operated differentially.
m) and (13n) relative axis operation means (20) for performing a relative rotation operation at a different angular velocity relative to each other by a required angle, comprising: The clutch mechanism (21) which is in the operating state and which is in the transmission cutoff state in the shaft relation changing operation is connected to the two rotating shafts (13m) and (13n) in parallel with the differential mechanism (15). Variable phase device interposed between them.
ア（１６）と、前記の他方側回転軸（１３ｎ）とともに
回転する第２ギア（１７）と、位置固定された状態で前
記第１ギア（１６）に対し咬合する第１遊星ギア（１６
ａ）と、前記第２ギア（１７）に対し咬合する第２遊星
ギア（１７ａ）と、前記第２ギア（１７）の周りでの前
記第２遊星ギア（１７ａ）の位置変更にかかわらず前記
第１遊星ギア（１６ａ）及び前記第２遊星ギア（１７
ａ）の両方に対して咬合する中間ギア（１８）とを備え
る遊星ギア式に構成し、 前記の軸関係操作手段（２０）は、 前記の軸関係保持操作として前記第２遊星ギア（１７
ａ）の位置を前記第２ギア（１７）の周りで固定する操
作と、前記の軸関係変更操作として前記第２遊星ギア
（１７ａ）の位置を前記第２ギア（１７）の周りで変更
する操作とを行う構成としてある請求項１記載の可変位
相装置。2. The differential mechanism (15) includes a first gear (16) rotating with the one-side rotation shaft (13m) and a second gear (16) rotating with the other-side rotation shaft (13n). 17) and a first planetary gear (16) that meshes with the first gear (16) in a fixed state.
a), a second planetary gear (17a) that meshes with the second gear (17), and the second planetary gear (17a) regardless of a change in position of the second planetary gear (17a) around the second gear (17). A first planetary gear (16a) and the second planetary gear (17
a) a planetary gear type including an intermediate gear (18) that meshes with both of the two planetary gears (17) as the axial relation maintaining operation.
The operation of fixing the position of a) around the second gear (17) and the position of the second planetary gear (17a) are changed around the second gear (17) as the axial relation changing operation. The variable phase device according to claim 1, wherein the variable phase device is configured to perform an operation.
に伴い自動的に伝動作用状態に切り換わり、かつ、回転
停止に伴い自動的に伝動遮断状態に切り換わる自動クラ
ッチ機構を採用した請求項１又は２記載の可変位相装
置。3. The automatic clutch mechanism according to claim 1, wherein said clutch mechanism automatically switches to a transmission operation state with rotation and automatically switches to a transmission cutoff state with rotation stop. Or the variable phase device according to 2.
ラッチ機構（２１）とを連係動作させる連係操作手段
（２２）を設けた請求項１又は２記載の可変位相装置。4. The variable phase device according to claim 1, further comprising a linking operation means (22) for linking the shaft-related operation means (20) and the clutch mechanism (21).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6324874A JP3005167B2 (en) | 1994-12-27 | 1994-12-27 | Variable phase device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6324874A JP3005167B2 (en) | 1994-12-27 | 1994-12-27 | Variable phase device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08177993A JPH08177993A (en) | 1996-07-12 |
| JP3005167B2 true JP3005167B2 (en) | 2000-01-31 |
Family
ID=18170607
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6324874A Expired - Fee Related JP3005167B2 (en) | 1994-12-27 | 1994-12-27 | Variable phase device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3005167B2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104061286A (en) * | 2014-07-09 | 2014-09-24 | 刘跃群 | Clutch device used for driving shaft and driven shaft with large rotation speed difference |
-
1994
- 1994-12-27 JP JP6324874A patent/JP3005167B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH08177993A (en) | 1996-07-12 |
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